JP6503901B2 - Scroll compressor - Google Patents

Description

    The present invention relates to a scroll compressor.

    As a compressor that compresses fluid, there is a scroll compressor.

    Patent Document 1 discloses a scroll compressor of this type. The scroll compressor includes a compression mechanism having a fixed scroll and a movable scroll. The fixed scroll includes a disk-shaped end plate, a cylindrical outer edge standing on the outer edge of the end plate, and a spiral wrap standing on the inside of the outer edge. The movable scroll has an end plate slidingly in contact with the outer edge portion of the fixed scroll or the tip of the wrap, and a wrap erected on the end plate. In the compression mechanism, the scrolls mesh with each other to form a compression chamber between the wraps. As the movable scroll performs eccentric rotational movement with respect to the fixed scroll, the volume of the compression chamber gradually decreases. As a result, the fluid is compressed in the compression chamber.

    In the scroll compressor, a stationary oil groove is formed at the end of the outer edge of the stationary scroll, and a movable oil groove is formed in the end plate of the movable scroll. A high pressure lubricating oil is supplied to the stationary oil groove. In the compression mechanism, the movable scroll performs an eccentric rotational movement, whereby a first state in which the movable oil groove communicates with the fixed oil groove and a second state in which the movable oil groove communicates with the fluid chamber (compression chamber) Repeat alternately. When the compression mechanism is in the first state, high-pressure lubricating oil in the stationary oil groove is supplied to the movable oil groove. This oil is used to lubricate the thrust surface between the outer edge of the fixed scroll and the end plate of the movable scroll. When the compression mechanism is in the second state, the movable oil groove is also supplied to the fluid chamber.

JP, 2012-202221, A

    In the compression mechanism disclosed in Patent Document 1, in the first state, the fixed oil groove and the movable oil groove overlap in the axial direction, and the two oil grooves communicate with each other. However, immediately before the two oil grooves communicate with each other, the internal pressure of the fixed oil groove is relatively high with respect to the internal pressure of the movable oil groove. In such a state, the high pressure inside the fixed side oil groove generates a separating force that pulls the movable scroll away from the fixed scroll, and a portion of the movable scroll's end plate corresponding to the fixed side oil groove is axially outside. It was confirmed that it was slightly deformed towards the Then, the internal pressure of the stationary oil groove is greatly reduced immediately before and immediately after the stationary oil groove and the movable oil groove communicate with each other, and the oil of the stationary oil groove is supplied to the movable oil groove. It will be difficult. Thus, a new problem has been found that if the supply of oil to the movable oil groove is insufficient, the lubrication of the thrust surface corresponding to the movable oil groove is impaired.

    The present invention has been made in view of such a point, and an object thereof is to propose a scroll compressor capable of more reliably supplying oil to a thrust surface between a fixed scroll and a movable scroll.

    The first invention is directed to a scroll type compressor, comprising a casing (20), a motor (30) housed inside the casing (20), and a compression mechanism (40) driven by the motor (30). And the compression mechanism (40) includes an end plate (61), an outer edge portion (63) erected on the outer edge of the end plate (61), and a wrap erected inside the outer edge portion (63). A fixed scroll (60) having (62), a mirror plate (71) on which respective tips of the wrap (62) and the outer edge portion (63) of the fixed scroll (60) are in sliding contact, And a movable scroll (70) having a wrap (72), and a contact surface (A1, A2) between the end plate (71) of the movable scroll (70) and the outer edge (63) of the fixed scroll (60) Constitute a thrust surface, and the wrap (72) of the movable scroll (70) and the wrap (62) of the fixed scroll (60) Between the fluid chamber (S) and the suction chamber (S1) where the fluid is sucked and the compression chamber (S2) where the fluid is compressed, and the mirror plate (71) of the movable scroll (70) A movable side oil groove (83) to which a high-pressure lubricating oil equivalent to the discharge pressure of the compression mechanism (40) is supplied is formed in a portion near the suction chamber (S1) on the contact surface (A2) of A stationary oil groove (80) to which a high pressure lubricating oil equivalent to the discharge pressure of the compression mechanism (40) is supplied is provided on the contact surface (A1) of the outer edge portion (63) of the stationary scroll (60). And the movable side oil groove (83).

    In the first aspect of the invention, the movable scroll (70) performs a pivoting motion (eccentric motion) with respect to the fixed scroll (60) by driving the compression mechanism (40) by the electric motor (30). In the compression mechanism (40), the outer edge (63) of the fixed scroll (60) contacts the end plate (71) of the movable scroll (70) to form thrust surfaces (A1, A2). At the same time, the wrap (72) of the movable scroll (70) and the wrap (62) of the fixed scroll (60) contact in the radial direction, and this contact portion (T) constitutes a seal portion. Thus, the fluid chamber (S) inside the compression mechanism (40) is divided into a suction chamber (S1) into which the fluid is sucked and a compression chamber (S2) into which the fluid is compressed. As the volume of the compression chamber (S2) gradually decreases, the fluid is compressed to a high pressure and discharged from the compression mechanism (40).

    In the present invention, the stationary oil groove (80) is formed in the contact surface (A1) of the outer edge portion (63) of the stationary scroll (60). The stationary oil groove (80) is supplied with high-pressure lubricating oil corresponding to the discharge pressure of the compression mechanism (40). As a result, the lubricating oil of the stationary oil groove (80) is supplied to the thrust surfaces (A1, A2) near the stationary oil groove (80).

    A movable oil groove (83) is formed on the contact surface (A2) of the end plate (71) of the movable scroll (70). The movable oil groove (83) is supplied with high-pressure lubricating oil corresponding to the discharge pressure of the compression mechanism (40). The movable oil groove (83) is independently provided without communicating with the fixed oil groove (80). Therefore, as described above, even if the internal pressure of the stationary oil groove (80) decreases, the lubricating oil can be reliably supplied from the movable oil groove (83) to the thrust surfaces (A1, A2) therearound.

    The movable scroll (70) is formed in the vicinity of the suction chamber (S1) of the compression mechanism (40). When the movable scroll (70) performs a pivoting motion, the positions of the suction chamber (S1) and the movable oil groove (83) become close to or separated from each other. If the movable oil groove (83) is always close to the suction chamber (S1), the high-pressure oil in the movable oil groove (83) flows only into the suction chamber (S1) with extremely low pressure. As a result, the lubrication of the thrust surface is lost. On the other hand, in the present invention, the movable oil groove (83) as well as the movable scroll (70) performs a pivoting motion. As a result, since the seal length between the movable oil groove (83) and the suction chamber (S1) can be secured to a certain extent, lubricating oil can be reliably applied to the thrust surfaces (A1, A2) around the movable oil groove (83). Can be supplied to

    According to a second aspect of the present invention, in the first aspect, the fixed oil groove (80) and the movable oil groove (83) are opposed to each other across the central portion in the radial direction of the fixed scroll (60). It is characterized in that it is formed.

    In the second aspect of the present invention, the fixed oil groove (80) and the movable oil groove (83) are opposed to each other across the radial center of the fixed scroll (60). As a result, the separating force of the stationary oil groove (80) by the high pressure oil and the separating force of the movable oil groove (83) by the high pressure oil can be easily balanced. As a result, since it is possible to prevent an increase in the overturning moment on the stationary-side oil groove (80) side, it is possible to suppress a decrease in the internal pressure of the stationary-side oil groove (80) as described above.

    The third invention is characterized in that in the second invention, the movable oil groove (83) is formed in a substantially arc shape extending along the suction chamber (S1).

    In the third invention, the movable oil groove (83) is formed in a substantially arc shape extending along the suction chamber (S1). As a result, the lubrication region of the thrust surfaces (A1, A2) near the suction chamber (S1) can be expanded. At this time, as described above, since the seal length between the movable oil groove (83) and the suction chamber (S1) can be secured, the oil of the movable oil groove (83) is supplied only to the suction chamber (S1). It can also be suppressed.

    In the fourth invention according to the third invention, in the stationary oil groove (80), both ends in the circumferential direction of the stationary oil groove (80) extend to the vicinity of the movable oil groove (83). It is characterized in that it is formed in a substantially arc shape.

    In the fourth invention, the fixed oil groove (80) is also formed in a substantially arc shape, and both ends in the circumferential direction extend to the vicinity of the movable oil groove (83). Thereby, the lubrication area of the thrust surface corresponding to the stationary oil groove (80) can be expanded. As a result, in the compression mechanism (40), high-pressure lubricating oil can be supplied over substantially the entire circumference of the thrust surface (A1, A2).

    In the first aspect of the invention, the stationary oil groove (80) and the movable oil groove (83) are not communicated with each other, and high-pressure lubricating oil is supplied from the oil grooves (80, 83). As a result, even if the internal pressure of the stationary oil groove (80) decreases, the lubricating oil can be reliably supplied to the thrust surface in the vicinity of the movable oil groove (83). Moreover, since the seal length between the movable oil groove (83) and the suction chamber (S1) can be secured, excessive supply of lubricating oil in the movable oil groove (83) to the suction chamber (S1) can be suppressed. The thrust surfaces (A1, A2) in the vicinity of the movable oil groove (83) can be lubricated more reliably.

    In the second aspect of the invention, since the fixed oil groove (80) and the movable oil groove (83) are positioned to face each other, the overturning moment can be reduced. As a result, a decrease in the internal pressure of the stationary oil groove (80) can be prevented, and the thrust surface in the vicinity of the stationary oil groove (80) can be reliably lubricated.

    In the third invention, since the movable side oil groove (83) is formed in a substantially arc shape along the suction chamber (S1), the lubrication region of the thrust surface (A1, A2) corresponding to the movable side oil groove (83) Can be enlarged. According to the fourth aspect of the present invention, the lubricating region of the thrust surface (A1, A2) corresponding to the stationary oil groove (80) can be expanded, and lubricating oil can be reliably supplied to substantially the entire circumference of the thrust surface (A1, A2).

FIG. 1 is a longitudinal sectional view of a scroll compressor according to an embodiment. FIG. 2 is a longitudinal sectional view of the main part of the scroll compressor according to the embodiment. FIG. 3 is a bottom view of the fixed scroll of the scroll compressor according to the embodiment, showing a state where the rotation angle of the movable scroll is 0 ° (360 °). FIG. 4 is a bottom view of the fixed scroll of the scroll compressor according to the embodiment, showing a state where the rotation angle of the movable scroll is 90 °. FIG. 5 is a bottom view of the fixed scroll of the scroll compressor according to the embodiment, in which the rotation angle of the movable scroll is 180 °. FIG. 6 is a bottom view of the fixed scroll of the scroll compressor according to the embodiment, in which the rotation angle of the movable scroll is 270 °.

    Hereinafter, embodiments of the present invention will be described in detail based on the drawings. The following embodiments are essentially preferred examples, and are not intended to limit the scope of the present invention, its applications, or its applications.

    As shown in FIGS. 1 and 2, the scroll compressor (10) (hereinafter, also simply referred to as a compressor (10)) of the present embodiment is provided in a refrigerant circuit of a vapor compression refrigeration cycle and is a fluid. The refrigerant is compressed. In the refrigerant circuit, the refrigerant compressed by the compressor (10) is condensed by the condenser, decompressed by the decompression mechanism, evaporated by the evaporator, and sucked into the compressor (10).

    The scroll compressor (10) comprises a casing (20) and a motor (30) and a compression mechanism (40) housed in the casing (20). The casing (20) is formed in a vertically long cylindrical shape and configured in a closed dome type.

    The motor (30) comprises a stator (31) fixed to the casing (20) and a rotor (32) arranged inside the stator (31). The drive shaft (11) passes through the rotor (32) and is fixed to the drive shaft (11).

    At the bottom of the casing (20) is formed an oil reservoir (21) in which lubricating oil is stored. The suction pipe (12) is penetrated in the upper part of the casing (20). The discharge pipe (13) is penetrated through the central portion of the casing (20).

    A housing (50) disposed above the electric motor (30) is fixed to the casing (20). A compression mechanism (40) is disposed above the housing (50). The inflow end of the discharge pipe (13) is located between the motor (30) and the housing (50).

    The drive shaft (11) extends vertically along the central axis of the casing (20). The drive shaft (11) has a main shaft portion (14) and an eccentric portion (15) connected to the upper end of the main shaft portion (14). The lower portion of the main shaft portion (14) is rotatably supported by the lower bearing (22) on the casing (20). The lower bearing (22) is fixed to the inner circumferential surface of the casing (20). The upper portion of the main shaft portion (14) penetrates the housing (50) and is rotatably supported by the upper bearing (51) of the housing (50). The upper bearing (51) is fixed to the inner peripheral surface of the casing (20).

    The compression mechanism (40) includes a fixed scroll (60) fixed to the upper surface of the housing (50) and a movable scroll (70) meshed with the fixed scroll (60). That is, the movable scroll (70) is disposed between the fixed scroll (60) and the housing (50) and installed in the housing (50).

    An annular portion (52) and a recess (53) are formed in the housing (50). The annular portion (52) is formed on the outer periphery of the housing (50). The recess (53) is formed in a central upper portion of the housing (50), and is formed in the shape of a dish whose center is recessed. An upper bearing (51) is formed below the recess (53).

   The housing (50) is fixed to the inside of the casing (20) by press fitting. That is, the inner peripheral surface of the casing (20) and the outer peripheral surface of the annular portion (52) of the housing (50) are airtightly attached over the entire periphery. The housing (50) divides the inside of the casing (20) into an upper space (23) in which the compression mechanism (40) is accommodated and a lower space (24) in which the electric motor (30) is accommodated.

    The fixed scroll (60) comprises an end plate (61) and a substantially cylindrical outer edge portion (63) erected on the outer edge of the front (the lower surface in FIGS. 1 and 2) of the end plate (61); And an involute wrap (62) standing on the inside of the outer edge (63). The end plate (61) is located on the outer peripheral side and is formed continuously with the wrap (62). The tip end surface of the wrap (62) and the tip end surface of the outer edge portion (63) are formed substantially flush. The fixed scroll (60) is fixed to the housing (50).

    The movable scroll (70) comprises an end plate (71), a spiral (involute form) wrap (72) formed on the front (upper surface in FIGS. 1 and 2) of the end plate (71), and an end plate (71) And a boss (73) formed at the center of the back of the The eccentric portion (15) of the drive shaft (11) is inserted into the boss portion (73), and the drive shaft (11) is connected.

    In the compression mechanism (40), a fluid chamber (S) into which the refrigerant flows is formed between the fixed scroll (60) and the movable scroll (70). The movable scroll (70) is disposed such that the wrap (72) meshes with the wrap (62) of the fixed scroll (60). A suction port (64) is formed at the outer edge (63) of the fixed scroll (60) (see FIG. 3). The downstream end of the suction pipe (12) is connected to the suction port (64).

    The fluid chamber (S) is divided into a suction chamber (S1) and a compression chamber (S2). That is, when the inner peripheral surface of the outer edge portion (63) of the fixed scroll (60) substantially contacts the outer peripheral surface of the wrap (72) of the movable scroll (70), suction is performed across the contact portion (T). A chamber (S1) and a compression chamber (S2) are divided (see, for example, FIG. 3). The suction chamber (S1) constitutes a space into which a low pressure refrigerant is drawn. The suction chamber (S1) communicates with the suction port (64) and is shut off from the compression chamber (S2). The compression chamber (S2) constitutes a space for compressing a low pressure refrigerant. The compression chamber (S2) is shut off from the suction chamber (S1).

    A discharge port (65) is formed at the center of the end plate (61) of the fixed scroll (60). A high pressure chamber (66) having a discharge port (65) opened is formed on the back surface (upper surface in FIGS. 1 and 2) of the end plate (61) of the fixed scroll (60). The high pressure chamber (66) communicates with the lower space (24) through a passage (not shown) formed in the end plate (61) of the fixed scroll (60) and the housing (50). The high pressure refrigerant compressed by the compression mechanism (40) flows out to the lower space (24). Therefore, the lower space (24) is configured in a high pressure atmosphere inside the casing (20).

    The compression mechanism (40) of the present embodiment is configured in an asymmetric spiral shape in which the wrap (62) of the fixed scroll (60) and the wrap (72) of the movable scroll (70) are asymmetrical. Specifically, in the compression mechanism (40), the total length of the spiral of the wrap (72) of the movable scroll (70) is larger than the total length of the spiral of the wrap (62) of the fixed scroll (60).

    An oil supply passage (16) extending in the vertical direction is formed in the drive shaft (11) from the lower end to the upper end of the drive shaft (11). The lower end of the drive shaft (11) is immersed in the oil reservoir (21). The oil supply passage (16) supplies the lubricating oil of the oil reservoir (21) to the lower bearing (22) and the upper bearing (51), and the lubricating oil is provided between the boss (73) and the drive shaft (11). Supply to the sliding surface. The oil supply passage (16) opens at the upper end surface of the drive shaft (11) and supplies lubricating oil above the drive shaft (11).

    The annular portion (52) of the housing (50) is provided with a seal member (43) on the upper surface of the inner peripheral portion. A back pressure portion (42) which is a high pressure space is formed inside the seal member (43). An intermediate pressure portion (44) which is an intermediate pressure space is formed outside the seal member. That is, the back pressure portion (42) is mainly configured by the recess (53) of the housing (50). The recess (53) communicates with the oil supply passage (16) of the drive shaft (11) through the inside of the boss (73) of the movable scroll (70). A high pressure equivalent to the discharge pressure of the compression mechanism (40) acts on the back pressure portion (42). The back pressure portion (42) presses the movable scroll (70) against the fixed scroll (60) by the high pressure.

    The intermediate pressure section (44) includes a movable pressure section (44a) and a fixed pressure section (44b). The movable side pressure portion (44a) is formed on the back surface of the end plate (71) of the movable scroll (70) near the outer peripheral side. The movable pressure portion (44a) is formed outside the back pressure portion (42), and presses the movable scroll (70) against the fixed scroll (60) by the intermediate pressure.

    The fixed pressure portion (44b) is formed outside the fixed scroll (60) in the upper space (23). The stationary pressure portion (44b) communicates with the movable pressure portion (44a) through the gap between the outer edge (63) of the end plate (61) of the stationary scroll (60) and the casing (20).

    An Oldham fitting (not shown) is provided at the top of the housing (50). The Oldham joint constitutes an anti-rotation member of the movable scroll (70).

<Oil supply line>
As shown in FIGS. 2 and 3, the compressor (10) includes a stationary oil supply passage (55) for supplying high-pressure oil (lubricating oil) to the stationary oil groove (80), and a movable oil groove 83) and a movable side oil supply passage (56) for supplying high pressure oil (lubricating oil).

[Fixed side oil supply passage]
As shown in FIG. 2, the fixed oil supply passage (55) has first to fifth oil passages (C 1 to C 5). The first oil passage (C1) radially penetrates the inside of the housing (50). The starting end (inflow end) of the first oil passage (C1) is in communication with the inside of the recess (53). The end of the first oil passage (C1) is closed to the inner circumferential surface of the casing (20).

    The second oil passage (C2) penetrates the inside of the housing (50) in the axial direction (vertical direction). The lower end of the second oil passage (C2) opens into the lower space (24), and the upper end of the second oil passage (C2) opens toward the lower surface of the outer edge (63) of the fixed scroll (60). The second oil passage (C2) is in communication with the first oil passage (C1) by intersecting the first oil passage (C1).

    A first screw member (76) extending in the axial direction (vertical direction) is inserted into the second oil passage (C2). The lower end portion of the first screw member (76) is formed with a head (76a) closing the opening of the lower end of the second oil passage (C2). A spiral groove (76b) having a spiral groove is formed in a portion near the upper portion of the first screw member (76). The spiral groove portion (76b) constitutes a throttling portion that narrows the flow path of the oil (lubricating oil) flowing through the second oil passage (C2).

    The third oil passage (C3) penetrates the outer edge portion (63) of the fixed scroll (60) in the axial direction (vertical direction). The opening at the lower end of the third oil passage (C3) communicates with the opening at the upper end of the second oil passage (C2). The opening at the upper end of the third oil passage (C3) is closed by the sealing member (77).

    The fourth oil passage (C4) extends radially around the outer edge (63) of the fixed scroll (60). An opening is formed at the radially outer end of the fourth oil passage (C4), and the opening is closed by a sealing member (78). The radially inner end of the fourth oil passage (C4) is located near the inner peripheral surface of the outer edge (63).

    The fifth oil passage (C5) extends downward from the radially inner end of the fourth oil passage (C4). The upper end of the fifth oil passage (C5) communicates with the fourth oil passage (C4), and the lower end of the fifth oil passage (C5) communicates with the stationary oil groove (80) (details will be described later).

[Movable side oil supply passage]
The movable side oil supply passage (56) has a sixth oil passage (C6), a seventh oil passage (C7), and an eighth oil passage (C8). The sixth oil passage (C6) is formed by an internal space of a recess formed at the upper end of the drive shaft (11).

    The seventh oil passage (C7) radially extends inside the end plate (71) of the movable scroll (70). An opening communicating with the sixth oil passage (C6) is formed at the beginning (a radially inward end) of the seventh oil passage (C7). The end (radially outward end) of the seventh oil passage (C7) opens toward the inner peripheral surface of the casing (20).

    The second screw member (79) is inserted into the seventh oil passage (C7). A head (79a) is formed at the radially outer end of the second screw member (79) to close the opening at the end of the seventh oil passage (C7). A spiral groove (79b) having a spiral groove is formed at a radially inward portion of the second screw member (79). The spiral groove portion (79b) constitutes a throttling portion that narrows the flow path of the oil (lubricating oil) flowing through the seventh oil passage (C7).

    The eighth oil passage (C8) is formed slightly radially outward of the end plate (71) of the movable scroll (70). The eighth oil passage (C8) is formed of, for example, a cylindrical round hole whose axis is directed up and down. The starting end of the eighth oil passage (C8) communicates with the flow passage on the downstream side of the spiral groove (79b) in the eighth oil passage (C8). The end of the eighth oil passage (C8) communicates with the movable oil groove (83).

<Configuration of fixed side oil groove and movable side oil groove>
[Fixed side oil groove]
The stationary oil groove (80) is in communication with the stationary oil supply passage (55). That is, the fixed oil groove (80) is supplied with high-pressure lubricating oil corresponding to the discharge pressure of the compression mechanism (40).

    As shown in FIGS. 2 and 3, a stationary oil groove (80) is formed on the front surface (the lower surface in FIG. 2) of the outer edge portion (63) of the stationary scroll (60). That is, the fixed oil groove (80) is located on the contact surface (A1) of the movable scroll (70) with the end plate (71) (hereinafter also referred to as a thrust surface) of the outer edge (63) of the fixed scroll (60). It is formed.

    The stationary oil groove (80) is a substantially circular shape along the outer peripheral surface of the fluid chamber (S) inside the compression mechanism (40) (ie, the inner peripheral surface of the outer edge (63) of the fixed scroll (60)). It is formed in an arc shape. The arc angle of the stationary-side oil groove (80) of the present embodiment is larger than 180 degrees and smaller than 270 degrees. The stationary oil groove (80) extends in an arc shape so as to extend over the first quadrant, the fourth quadrant, and the third quadrant in FIG. Here, each quadrant is determined based on the reference line X shown in FIG. That is, the reference line X is a reference line Y when a reference line connecting the vicinity of the inner edge of the suction port 64 (the end on the outermost periphery of the fluid chamber) and the discharge port (65) in the radial direction is Y. And 90 degrees in the circumferential direction. Here, one end (end on the right side in FIG. 3) of the fixed-side oil groove (80) in the longitudinal direction is positioned slightly closer to the second quadrant of the first quadrant. The other longitudinal end (left end in FIG. 3) of the fixed oil groove (80) is located near the second quadrant of the third quadrant.

    The stationary oil groove (80) is always positioned inward of the trajectory of the 360 degree pivoting movement of the end plate (71) of the movable scroll (70). Accordingly, the stationary oil groove (80) always faces the end plate (71) of the movable scroll (70).

[Movable side oil groove]
The movable oil groove (83) communicates with the movable oil supply passage (56). That is, the movable oil groove (83) is supplied with high-pressure lubricating oil corresponding to the discharge pressure of the compression mechanism (40).

    As shown in FIGS. 2 and 3, a movable oil groove (83) is formed on the front surface (upper surface in FIG. 2) of the end plate (71) of the movable scroll (70). That is, the movable-side oil groove (83) is on the contact surface (A2) (hereinafter also referred to as a thrust surface) with the outer edge portion (63) of the fixed scroll (60) of the end plate (71) of the movable scroll (70). It is formed.

    The movable oil groove (83) is formed in a substantially arc shape along the suction port (64) inside the compression mechanism (40) and a part of the suction chamber (S1). The arc angle of the movable-side oil groove (83) of the present embodiment is smaller than 90 degrees. The movable oil groove (83) is located in the second quadrant in FIG. The movable oil groove (83) performs a pivoting movement (eccentric movement) with the movable scroll (70). The movable oil groove (83) always faces the outer edge (63) of the fixed scroll (60), even if it performs a 360 degree pivoting movement. In addition, the movable oil groove (83) does not always communicate with the stationary oil groove (80) and the fluid chamber (S) even if it performs a 360 ° pivotal movement.

    The movable oil groove (83) is formed at a position facing the stationary oil groove (80) across the radial center of the fixed scroll (60) (ie, the center C of the discharge port (65)). Specifically, the circumferential center (P1 in FIG. 3) of the movable oil groove (83), the circumferential center (P2 in FIG. 3) of the fixed oil groove (80), and the discharge port (65) And the center C of) is disposed on substantially the same line in the radial direction.

-Driving operation-
First, the basic operation of the compressor (10) will be described.

    When the motor (30) is operated, the movable scroll (70) of the compression mechanism (40) is rotationally driven. Since the movable scroll (70) is prevented from rotating by the rotation preventing member, the movable scroll (70) performs only eccentric rotation around the axis of the drive shaft (11). As shown in FIGS. 3 to 6, when the eccentric rotation of the movable scroll (70) rotates, the fluid chamber (S) is divided into a suction chamber (S1) and a compression chamber (S2) via the contact portion (T). Be done. A plurality of compression chambers (S2) are formed between the wrap (62) of the fixed scroll (60) and the wrap (72) of the movable scroll (70). When the movable scroll (70) eccentrically rotates, the compression chambers (S2) gradually approach the center (discharge port (65)) and the volumes of the compression chambers (S2) decrease. Thus, the refrigerant is compressed in each compression chamber (S2).

    When the compression chamber (S2) having the minimum volume communicates with the discharge port (65), the high pressure gas refrigerant in the compression chamber (S2) is discharged to the high pressure chamber (66) through the discharge port (65). The high pressure refrigerant gas of the high pressure chamber (66) flows out to the lower space (24) via the fixed scroll (60) and the respective passages formed in the housing (50). The high pressure gas refrigerant in the lower space (24) is discharged to the outside of the casing (20) through the discharge pipe (13).

-Refueling operation-
Next, the lubricating oil supplying operation of the compressor (10) will be described in detail with reference to FIGS.

    When the high pressure gas refrigerant flows out to the lower space (24) of the compressor (10), the lower space (24) becomes a high pressure atmosphere, and the lubricating oil in the oil reservoir (21) also becomes a high pressure state. The high pressure lubricating oil of the oil reservoir (21) flows upward through the oil supply passage (16) of the drive shaft (11), and the upper end portion of the eccentric portion (15) of the drive shaft (11) C6) spills out.

    A portion of the oil in the sixth oil passage (C6) is supplied to the sliding surfaces of the eccentric portion (15) of the drive shaft (11) and the boss portion (73). Thereby, the back pressure part (42) becomes a high pressure atmosphere corresponding to the discharge pressure of the compression mechanism (40). The movable scroll (70) is pressed against the fixed scroll (60) by the high pressure of the back pressure portion (42).

    The high pressure oil accumulated in the back pressure portion (42) is transferred to the first oil passage (C1), the second oil passage (C2), the third oil passage (C3), the fourth oil passage (C4), and the fifth oil. It flows through the passage (C5) in order and flows out to the stationary oil groove (80). As a result, high-pressure lubricating oil corresponding to the discharge pressure of the compression mechanism (40) is supplied to the fixed oil groove (80).

    At the same time, part of the oil in the sixth oil passage (C6) flows through the seventh oil passage (C7) and the eighth oil passage (C8) in order and flows into the movable oil groove (83).

    As shown in FIG. 3 to FIG. 6, while the movable scroll (70) is performing an orbiting motion, the oil of the stationary oil groove (80) is supplied to the thrust surfaces (A1, A2) around it. It is used to lubricate the thrust surfaces (A1, A2). That is, the oil of the stationary-side oil groove (80) is mainly used for lubricating the portions of the thrust surfaces (A1, A2) corresponding to the first quadrant, the third quadrant, and the fourth quadrant. Even if the movable scroll (70) performs a 360-degree turning motion, the stationary oil groove (80) and the movable oil groove (83) do not communicate with each other.

    On the other hand, the movable oil groove (83) changes its relative position to the fixed scroll (60) as the movable scroll (70) pivots.

    Specifically, in the state shown in FIG. 3 (rotation angle = 0 ° (360 °), the position of the movable oil groove (83) is relatively close to the suction chamber (S1). The oil in the movable oil groove (83) is easily sucked into the suction chamber (S1), and for example, the inner surface of the movable oil groove (83) is decreased, or the thrust surface (peripheral side of the movable oil groove (83)) It becomes easy to reduce the oil supply to A1, A2).

    On the other hand, in the state of FIG. 4 (rotation angle = 90 °) and FIG. 5 (rotation angle = 180 °), the position of the movable oil groove (83) is relatively far from the suction chamber (S1) Become. Therefore, in this state, the oil in the movable oil groove (83) can be prevented from being sucked into the suction chamber (S1). Further, by displacing the movable side oil groove (83) toward the outer periphery of the outer edge portion (63) in this manner, the lubrication of oil on the thrust surfaces (A1, A2) corresponding to this position can be promoted.

    Furthermore, in the state of FIG. 6 (rotation angle = 270 °), the position of the movable oil groove (83) approaches the suction chamber (S1) again. As described above, the movable oil groove (83) reciprocates in and out of the radial direction each time the movable scroll (70) makes one rotation, thereby suppressing a drop in the internal pressure of the movable oil groove (83) and moving the movable oil groove (83). The lubricating region of the thrust surface (A1, A2) by the oil of the side oil groove (83) can be expanded.

-Effect of the embodiment-
The following effects are achieved in the above embodiment.

    The stationary oil groove (80) and the movable oil groove (83) are not communicated with each other, and high-pressure lubricating oil is supplied from the respective oil grooves (80, 83). As a result, even if the internal pressure of the fixed oil groove (80) decreases, the lubricating oil can be reliably supplied to the thrust surfaces (A1, A2) near the movable oil groove (83). Moreover, since the seal length between the movable oil groove (83) and the suction chamber (S1) can be secured at the positions of FIG. 4 and FIG. 5, the lubricating oil of the movable oil groove (83) is the suction chamber (S1). It is possible to suppress excessive supply to the upper and lower thrust surfaces (A1, A2) in the vicinity of the movable-side oil groove (83) more reliably.

    Since the fixed side oil groove (80) and the movable side oil groove (83) face each other, the overturning moment can be reduced. As a result, a decrease in the internal pressure of the stationary oil groove (80) can be prevented, and the thrust surfaces (A1, A2) near the stationary oil groove (80) can be reliably lubricated.

    Since the movable side oil groove (83) is formed in a substantially arc shape along the suction chamber (S1), the lubricating region of the thrust surface (A1, A2) corresponding to the movable side oil groove (83) can be expanded. Furthermore, since the fixed side oil groove (80) is formed in a substantially arc shape straddling three quadrants, the lubricating region of the thrust surface (A1, A2) corresponding to the fixed side oil groove (80) can also be expanded. Lubricating oil can be reliably supplied to substantially the entire circumference of (A1, A2).

Other Embodiments
The fixed-side oil groove (80) and the movable-side oil groove (83) may be in the form of a vertically long straight line, an oval or the like, and are not limited to the arc shape.

    The compression mechanism (40) is not necessarily limited to the asymmetrical spiral, but may be a symmetrical spiral.

    As described above, the present invention is useful for scroll compressors.

10 scroll compressor
20 casing
30 motor
40 compression mechanism
60 Fixed Scroll
61 end plate
62 lap
63 Outer edge
70 Movable Scroll
71 end plate
72 laps
80 Fixed oil groove
83 Movable oil groove
S fluid chamber
S1 Suction chamber
S2 compression chamber
A1 Contact surface (thrust surface)
A2 contact surface (thrust surface)

Claims (4)

A scroll type compressor,
A casing (20),
An electric motor (30) housed inside the casing (20);
A compression mechanism (40) driven by the motor (30);
The compression mechanism (40)
A fixed scroll (60) having an end plate (61), an outer edge portion (63) erected at the outer edge of the end plate (61), and a wrap (62) erected inside the outer edge portion (63); Movable scroll (70) having a mirror plate (71) on which the tips of the wrap (62) and the outer edge portion (63) of the fixed scroll (60) come into sliding contact, and a wrap (72) And the contact surface (A1, A2) between the end plate (71) of the movable scroll (70) and the outer edge portion (63) of the fixed scroll (60) constitutes a thrust surface, and the movable scroll (70) Fluid chamber (S) between the wrap (72) of the above and the wrap (62) of the fixed scroll (60), a suction chamber (S1) into which the fluid is sucked and a compression chamber (S2) into which the fluid is compressed And are configured to partition
A high pressure lubricating oil equivalent to the discharge pressure of the compression mechanism (40) is supplied to the contact surface (A2) of the end plate (71) of the movable scroll (70) near the suction chamber (S1) Movable oil groove (83) is formed.
In the contact surface (A1) of the outer edge portion (63) of the fixed scroll (60), a fixed oil groove (80) to which high-pressure lubricating oil corresponding to the discharge pressure of the compression mechanism (40) is supplied is A scroll compressor characterized in that it does not always communicate with the movable oil groove (83). In claim 1,
The fixed oil groove (80) and the movable oil groove (83) are formed at positions opposed to each other across the central portion in the radial direction of the fixed scroll (60). Machine. In claim 2,
The scroll type compressor characterized in that the movable side oil groove (83) is formed in a substantially arc shape extending along the suction chamber (S1). In claim 3,
The stationary oil groove (80) is formed in a substantially arc shape in which both ends in the circumferential direction of the stationary oil groove (80) extend to the vicinity of the movable oil groove (83). Scroll type compressor.

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