Scroll compressor and refrigeration device

Abstract

By appropriately setting the timing of the pressure fluctuation in the intermediate pressure chamber and the timing of the pressure fluctuation in the fixed side oil groove, an increase in thrust surface pressure is suppressed. [Solution] The intermediate pressure port (49) overlaps with the intermediate pressure passage (48) in a predetermined angular range in which the movable scroll (70) orbits, as viewed in the axial direction. The movable oil groove (85) communicates with the compression chamber (S) in a predetermined angular range in which the movable scroll (70) orbits, as viewed in the axial direction. The communication state between the movable oil groove (85) and the compression chamber (S) ends before the end of a communication section in which the intermediate pressure port (49) communicates with the intermediate pressure passage (48).

Description

[Technical field]

[0001] The present disclosure relates to a scroll compressor and a refrigeration device. [Background technology]

[0002] Patent Document 1 discloses a scroll compressor including a compression mechanism having a fixed scroll and a movable scroll, and an intermediate pressure section that applies intermediate pressure to a part of the back surface of the movable scroll.

[0003] In the invention of Patent Document 1, the movable oil groove of the movable scroll is connected to the fixed oil groove and is connected to the outermost peripheral portion of the wrap groove of the fixed scroll when the wrap groove is in a state where the refrigerant is being sucked in, and is disconnected from the wrap groove when the wrap groove is in a state where a compression chamber is formed. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 5691352 Summary of the Invention [Problem to be solved by the invention]

[0005] Here, if the section where the movable side oil groove communicates with the compression chamber and the pushing force due to the pressure of the fixed side oil groove decreases coincides with the section in the latter half of the intermediate pressure communication section where the intermediate pressure chamber pressure increases and the pushing force increases, the thrust surface pressure will increase locally, which may deteriorate the sliding condition.

[0006] An object of the present disclosure is to suppress an increase in thrust surface pressure by appropriately setting the timing of pressure fluctuations in the intermediate pressure chamber and the timing of pressure fluctuations in the fixed side oil groove. [Means for solving the problem]

[0007] A first aspect of the present disclosure is a scroll compressor including a fixed scroll (60) having a fixed-side wrap (62) and a fixed-side end plate (61), and a movable scroll (70) having a movable-side wrap (72) and a movable-side end plate (71), in which a compression chamber (S) is formed by meshing the fixed-side wrap (62) and the movable-side wrap (72), the fixed-side end plate (61) is provided with a fixed-side oil groove (80) formed on a surface facing the movable-side end plate (71) and an intermediate pressure passage (48) communicating with a space in the compression chamber (S) through which an intermediate-pressure refrigerant flows, the intermediate-pressure refrigerant having a pressure higher than that of suction refrigerant and lower than that of discharge refrigerant, and the movable-side end plate (71) is provided with a fixed-side oil groove (80) formed on a surface facing the movable-side end plate (71). A movable-side oil groove (85) is formed on the opposing surface, and an intermediate pressure port (49) is provided which communicates with an intermediate pressure chamber (43) provided on the movable-side end plate (71) opposite the fixed-side end plate (61), and the intermediate pressure port (49) overlaps with the intermediate pressure passage (48) in a predetermined angular range in which the movable scroll (70) orbits, as viewed in the axial direction, and the movable-side oil groove (85) communicates with the compression chamber (S) in a predetermined angular range in which the movable scroll (70) orbits, as viewed in the axial direction, and the communication state between the movable-side oil groove (85) and the compression chamber (S) ends before the end of a communication section in which the intermediate pressure port (49) communicates with the intermediate pressure passage (48).

[0008] In the first aspect, the timing at which the pressing force pressing the movable scroll (70) toward the fixed scroll (60) increases due to pressure fluctuations in the intermediate pressure chamber (43) and the timing at which the pushing force pushing the movable scroll (70) away from the fixed scroll (60) increases due to pressure fluctuations in the fixed side oil groove (80) can be made to coincide with each other, thereby suppressing an increase in thrust surface pressure.

[0009] In a second aspect of the present disclosure, in the scroll compressor of the first aspect, a communication state between the movable side oil groove (85) and the compression chamber (S) begins after the start of the communication section in which the intermediate pressure port (49) is connected to the intermediate pressure passage (48).

[0010] In the second aspect, the increase in thrust surface pressure can be suppressed at an appropriate timing.

[0011] A third aspect of the present disclosure is the scroll compressor of the first or second aspect, wherein the movable oil groove (85) and the compression chamber (S) communicate with each other in an angle range of 50% or more of the communication section.

[0012] In the third aspect, it is possible to suppress an increase in thrust surface pressure in a predetermined angle range in the communication section.

[0013] A fourth aspect of the present disclosure is a scroll compressor according to any one of the first to third aspects, in which the communication state between the movable-side oil groove (85) and the compression chamber (S) ends in an angle range greater than 0° and not greater than 30° before the communication ends.

[0014] In the fourth aspect, it is possible to suppress an increase in thrust surface pressure in a predetermined angle range before the end of communication.

[0015] A fifth aspect of the present disclosure is a scroll compressor according to any one of the second to fourth aspects, in which the communication state between the movable oil groove (85) and the compression chamber (S) starts in an angle range of 0° or more and 10° or less after the communication starts.

[0016] In the fifth aspect, it is possible to suppress an increase in thrust surface pressure in a predetermined angle range after the start of communication.

[0017] A sixth aspect of the present disclosure is a refrigeration system including the scroll compressor (10) of any one of the first to fifth aspects, and a refrigerant circuit (1a) through which a refrigerant compressed by the scroll compressor (10) flows.

[0018] In a sixth aspect, a refrigeration system including a scroll compressor (10) and a refrigerant circuit (1a) can be provided. [Brief description of the drawings]

[0019] [Figure 1]FIG. 1 is a refrigerant circuit diagram showing the configuration of a refrigeration device according to this embodiment. [Diagram 2] FIG. 2 is a vertical sectional view showing the configuration of the scroll compressor. [Diagram 3] FIG. 3 is a bottom view showing the configuration of the fixed scroll. [Figure 4] FIG. 4 is a plan view showing the configuration of the movable scroll. [Diagram 5] FIG. 5 is a plan view showing the timing at which the space outside the movable scroll is completely closed off from the intake port. [Figure 6] FIG. 6 is a graph showing the relationship between the crank angle of the drive shaft and the pressure in the compression chamber, the pressure in the intermediate pressure chamber, the pressure in the fixed side oil groove, and the thrust surface pressure. [Figure 7] FIG. 7 is a plan view showing the timing immediately before the intermediate pressure port communicates with the intermediate pressure passage. [Figure 8] FIG. 8 is a plan view showing the timing after a portion of the intermediate pressure port communicates with the intermediate pressure passage. [Figure 9] FIG. 9 is a plan view showing the timing when the entire intermediate pressure port communicates with the intermediate pressure passage. [Figure 10] FIG. 10 is a plan view showing a timing before the end of the intermediate pressure communication section when a part of the intermediate pressure port is in communication with the intermediate pressure passage. [Figure 11] FIG. 11 is a plan view showing the timing immediately after the intermediate pressure port is separated from the intermediate pressure passage. [Figure 12] FIG. 12 is a graph showing the relationship between the crank angle of the drive shaft and the groove pressure and intermediate pressure. [Figure 13] FIG. 13 is a graph showing the relationship between the crank angle of the drive shaft and the pressure in the compression chamber, the pressure in the intermediate pressure chamber, the pressure in the fixed side oil groove, and the thrust surface pressure in the comparative example. [Figure 14] FIG. 14 is a graph showing the relationship between the crank angle of the drive shaft and the groove pressure and the intermediate pressure in the comparative example. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0020] As shown in Fig. 1, the scroll compressor (10) is provided in a refrigeration system (1). The refrigeration system (1) has a refrigerant circuit (1a) filled with a refrigerant. The refrigerant circuit (1a) has the scroll compressor (10), a radiator (3), a pressure reduction mechanism (4), and an evaporator (5). The pressure reduction mechanism (4) is, for example, an expansion valve. The refrigerant circuit (1a) performs a vapor compression refrigeration cycle.

[0021] The refrigeration system (1) is an air conditioner. The air conditioner may be a cooling only machine, a heating only machine, or an air conditioner that switches between cooling and heating. In this case, the air conditioner has a switching mechanism (e.g., a four-way switching valve) that switches the circulation direction of the refrigerant. The refrigeration system (1) may be a water heater, a chiller unit, a cooling device that cools the air inside a storage unit, or the like. The cooling device cools the air inside a refrigerator, a freezer, a container, or the like.

[0022] As shown in Fig. 2, the scroll compressor (10) includes a casing (20), an electric motor (30), and a compression mechanism (40). The casing (20) is formed in a vertically elongated cylindrical shape and configured as a sealed dome type. The casing (20) accommodates the electric motor (30) and the compression mechanism (40).

[0023] The electric motor (30) has a stator (31) and a rotor (32). The stator (31) is fixed to an inner circumferential surface of the casing (20). The rotor (32) is disposed inside the stator (31). The drive shaft (11) passes through the rotor (32). The rotor (32) is fixed to the drive shaft (11).

[0024] An oil reservoir (21) is provided at the bottom of the casing (20). Oil is stored in the oil reservoir (21). A suction pipe (12) is connected to the top of the casing (20). A discharge pipe (13) is connected to the body of the casing (20).

[0025] A housing (50) is fixed to the casing (20). The housing (50) is fixed inside the casing (20) by, for example, shrink fitting. The housing (50) is disposed above the electric motor (30). The compression mechanism (40) is disposed above the housing (50). The inlet end of the discharge pipe (13) is located between the electric motor (30) and the housing (50).

[0026] A recess (53) is formed in the housing (50). The recess (53) is formed by depressing a portion of the upper surface of the housing (50). An upper bearing (51) is provided below the recess (53).

[0027] The drive shaft (11) extends in the vertical direction along the central axis of the casing (20). The drive shaft (11) has a main shaft portion (14) and an eccentric portion (15).

[0028] The eccentric portion (15) is provided at the upper end of the main shaft portion (14). A lower portion of the main shaft portion (14) is rotatably supported by a lower bearing (22). The lower bearing (22) is fixed to the inner circumferential surface of the casing (20). For example, a positive displacement pump (25) is provided in the lower bearing (22). An upper portion of the main shaft portion (14) passes through the housing (50) and is rotatably supported by an upper bearing (51) of the housing (50).

[0029] The compression mechanism (40) includes a fixed scroll (60) and a movable scroll (70). The fixed scroll (60) is fixed to an upper surface of the housing (50). The movable scroll (70) is disposed between the fixed scroll (60) and the housing (50).

[0030] The fixed scroll (60) has a fixed end plate (61), a fixed side wrap (62), and an outer circumferential wall (63). The outer circumferential wall (63) is formed in a substantially cylindrical shape. The outer circumferential wall (63) stands on the outer edge of the front surface (the lower surface in FIG. 2) of the fixed end plate (61).

[0031] The fixed-side wrap (62) is formed in a spiral shape and is provided upright inside the outer circumferential wall (63) of the fixed-side end plate (61).

[0032] The fixed side end plate (61) is located on the outer periphery side and is formed continuously with the fixed side wrap (62). The tip surface of the fixed side wrap (62) and the tip surface of the outer periphery wall (63) are formed to be substantially flush with each other. The fixed scroll (60) is fixed to the housing (50).

[0033] The movable scroll (70) has a movable end plate (71), a movable wrap (72), and a boss portion (73). The movable wrap (72) is formed in a spiral shape. The movable wrap (72) is formed on the upper surface of the movable end plate (71). The movable wrap (72) meshes with the fixed wrap (62).

[0034] The boss portion (73) is formed at the center of the lower surface of the movable end plate (71). The eccentric portion (15) of the drive shaft (11) is inserted into the boss portion (73) to couple the drive shaft (11).

[0035] An Oldham coupling (45) is provided at the upper part of the housing (50). The Oldham coupling (45) prevents the movable scroll (70) from rotating on its axis. The Oldham coupling (45) is provided with a key (46). The key (46) protrudes from the lower surface of the movable end plate (71) of the movable scroll (70). A key groove (47) is formed in the lower surface of the movable end plate (71) of the movable scroll (70). The key (46) of the Oldham coupling (45) is slidably fitted into the key groove (47).

[0036] Although not shown, a key is also provided on the housing (50) side of the Oldham coupling (45), and the key on the housing (50) side is slidably fitted into a key groove (not shown) of the housing (50).

[0037] The compression mechanism (40) has a compression chamber (S) into which the refrigerant flows. The compression chamber (S) is formed between a fixed scroll (60) and a movable scroll (70). The movable scroll (70) is disposed such that a movable wrap (72) meshes with a fixed wrap (62) of the fixed scroll (60). Here, a lower surface of an outer peripheral wall (63) of the fixed scroll (60) serves as a thrust surface for the movable scroll (70). In addition, an upper surface of a movable end plate (71) of the movable scroll (70) serves as a thrust surface for the fixed scroll (60).

[0038] A suction port (64) is formed in the outer peripheral wall (63) of the fixed scroll (60). The suction port (64) opens near the end of the fixed side wrap (62). The downstream end of the suction pipe (12) is connected to the suction port (64).

[0039] A discharge port (65) is formed in the center of the fixed end plate (61) of the fixed scroll (60). The discharge port (65) opens in an upper surface of the fixed end plate (61) of the fixed scroll (60). High-pressure gas refrigerant discharged from the discharge port (65) flows into the lower space (24) through a passage (not shown) formed in the housing (50).

[0040] An oil supply passage (16) is formed inside the drive shaft (11). The oil supply passage (16) extends vertically from the lower end to the upper end of the drive shaft (11). The lower end of the drive shaft (11) is connected to a pump (25). The lower end of the pump (25) is immersed in an oil reservoir (21). The pump (25) draws up oil from the oil reservoir (21) as the drive shaft (11) rotates, and transports the oil to the oil supply passage (16). The oil supply passage (16) supplies oil from the oil reservoir (21) to the sliding surfaces between the lower bearing (22) and the drive shaft (11) and between the upper bearing (51) and the drive shaft (11), and also to the sliding surface between the boss portion (73) and the drive shaft (11). The oil supply passage (16) opens into the upper end surface of the drive shaft (11) and supplies oil to the upper portion of the drive shaft (11).

[0041] The recess (53) of the housing (50) communicates with the oil supply passage (16) of the drive shaft (11) through the inside of the boss portion (73) of the movable scroll (70). When high-pressure oil is supplied to the recess (53), a high pressure corresponding to the discharge pressure of the compression mechanism (40) acts on the recess (53). The movable scroll (70) is pressed against the fixed scroll (60) by the high pressure of the recess (53) and the intermediate pressure of an intermediate pressure chamber (43) described later.

[0042] An oil passage (55) is formed inside the housing (50) and the fixed scroll (60). An inflow end of the oil passage (55) communicates with the recess (53) of the housing (50). An outflow end of the oil passage (55) opens to the thrust surface of the fixed scroll (60). The oil passage (55) supplies high-pressure oil in the recess (53) to the thrust surface between the movable end plate (71) of the movable scroll (70) and the outer circumferential wall (63) of the fixed scroll (60).

[0043] An intermediate pressure passage (48) and a fixed-side oil groove (80) are formed in the lower surface of the outer circumferential wall (63) of the fixed scroll (60) (see FIG. 3). The inner end of the intermediate pressure passage (48) opens into the inner circumferential surface of the outer circumferential wall (63). The intermediate pressure passage (48) communicates with a space in the compression chamber (S) through which an intermediate-pressure refrigerant flows, the intermediate-pressure refrigerant having a pressure higher than that of the suction refrigerant and lower than that of the discharge refrigerant.

[0044] The fixed-side oil groove (80) is formed in a thrust surface of the outer circumferential wall (63) of the fixed-side end plate (61) that faces the movable-side end plate (71). The fixed-side oil groove (80) extends in the circumferential direction along the inner circumferential surface of the outer circumferential wall (63) of the fixed scroll (60). The fixed-side oil groove (80) is in communication with the oil passage (55), and oil is supplied from the oil passage (55) to the fixed-side oil groove (80).

[0045] An intermediate pressure chamber (43) is provided between the movable scroll (70) and the housing (50). The intermediate pressure chamber (43) is provided on the movable end plate (71) opposite the fixed end plate (61). The intermediate pressure chamber (43) is provided radially outward of the recess (53) of the housing (50).

[0046] An intermediate pressure port (49) is formed in the outer periphery of the movable end plate (71) of the movable scroll (70) (see FIG. 4). The intermediate pressure port (49) is a through hole that passes through the movable end plate (71) in the vertical direction. The intermediate pressure port (49) overlaps with the intermediate pressure passage (48) in a predetermined angular range in which the movable scroll (70) orbits, as viewed in the axial direction.

[0047] The intermediate pressure port (49) has an upper end intermittently connected to the outer end of the intermediate pressure passage (48), and a lower end thereof connected to the intermediate pressure chamber (43) between the movable scroll (70) and the housing (50). In other words, intermediate-pressure refrigerant is intermittently supplied from the compression chamber (S) in an intermediate-pressure state to the intermediate pressure chamber (43), and the intermediate pressure chamber (43) is maintained at a predetermined intermediate pressure.

[0048] A movable oil groove (85) is formed in a thrust surface of the movable end plate (71) facing the fixed end plate (61). The movable oil groove (85) communicates with the fixed oil groove (80) and the compression chamber (S) in a predetermined angular range in which the movable scroll (70) orbits, as viewed in the axial direction.

[0049] - Driving operation - The basic operation of the scroll compressor (10) will be described. In Fig. 2, when the electric motor (30) is operated, the drive shaft (11) to which the rotor (32) is fixed is rotated. The movable scroll (70) is prevented from rotating by the Oldham coupling (45), and therefore revolves around the axis of the drive shaft (11).

[0050] When the movable scroll (70) orbits, the refrigerant is compressed in the compression chamber (S). The high-pressure gas refrigerant compressed in the compression chamber (S) is discharged from the discharge port (65) and flows into the lower space (24) through a passage (not shown) 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).

[0051] As the drive shaft (11) rotates, the high-pressure oil in the oil reservoir (21) is sucked up by the pump (25), flows upward through the oil supply passage (16) of the drive shaft (11), and flows out from the opening at the upper end of the eccentric portion (15) of the drive shaft (11) into the inside of the boss portion (73) of the movable scroll (70).

[0052] The oil supplied to the boss portion (73) flows out into the recessed portion (53) of the housing (50) through a gap between the eccentric portion (15) of the drive shaft (11) and the boss portion (73). As a result, the recessed portion (53) of the housing (50) is subjected to a high pressure equivalent to the discharge pressure of the compression mechanism (40). The high pressure in the recessed portion (53) and the intermediate pressure in the intermediate pressure chamber (43) press the movable scroll (70) against the fixed scroll (60).

[0053] The high-pressure oil accumulated in the recess (53) flows through the oil passage (55) and out into the fixed-side oil groove (80). As a result, high-pressure oil equivalent to the discharge pressure of the compression mechanism (40) is supplied to the fixed-side oil groove (80).

[0054] <Thrust surface pressure> The thrust surface pressure acting on the sliding surfaces between the fixed scroll (60) and the movable scroll (70) is determined by the difference between the load pushing the movable scroll (70) downward and the load pressing the movable scroll (70) upward.

[0055] Specifically, the load pushing the movable scroll (70) downward is the sum of the pushing force due to the pressure in the compression chamber (S) and the pushing force due to the fixed-side oil groove (80). The load pressing the movable scroll (70) upward is the sum of the pressing force due to the high pressure in the recess (53) of the housing (50) and the pressing force due to the intermediate pressure in the intermediate pressure chamber (43).

[0056] Here, if, during the orbital movement of the movable scroll (70), a section in which the movable-side oil groove (85) communicates with the compression chamber (S) and the pushing force due to the pressure of the fixed-side oil groove (80) decreases coincides with a section in the latter half of the intermediate pressure communication section in which the pressure in the intermediate pressure chamber (43) increases and the pushing force increases, the thrust surface pressure will increase locally, which may deteriorate the sliding condition.

[0057] Therefore, in this embodiment, the timing of the pressure fluctuation in the intermediate pressure chamber (43) and the timing of the pressure fluctuation in the fixed side oil groove (80) are appropriately set, thereby suppressing an increase in the thrust surface pressure.

[0058] Specifically, as shown in FIG. 5, a case will be described in which the suction closing angle of the space outside the movable side wrap (72) in the compression chamber (S) is set to 0° and the movable scroll (70) is rotated counterclockwise.

[0059] As shown in Fig. 6, the angle θ1 is the timing at which the space outside the movable scroll (70) is completely closed off (see Fig. 5). At the angle θ1, the intermediate pressure port (49) does not communicate with the intermediate pressure passage (48). In addition, the movable oil groove (85) does not communicate with the compression chamber (S).

[0060] The angle θ2 is the timing immediately before the intermediate pressure port (49) communicates with the intermediate pressure passage (48) (see FIG. 7). At the angle θ2, the intermediate pressure port (49) does not communicate with the intermediate pressure passage (48). In addition, the movable-side oil groove (85) does not communicate with the compression chamber (S). From the angle θ2 to the angle θ3, the intermediate pressure port (49) communicates with the intermediate pressure passage (48).

[0061] The angle θ3 is the timing after part of the intermediate pressure port (49) communicates with the intermediate pressure passage (48) (see FIG. 8). At the angle θ3, the intermediate pressure port (49) communicates with the intermediate pressure passage (48). Also, the movable-side oil groove (85) does not communicate with the compression chamber (S). From the angle θ3 to the angle θ4, the movable-side oil groove (85) communicates with the compression chamber (S).

[0062] In this manner, communication between the movable-side oil groove (85) and the compression chamber (S) begins after the start of the communication section in which the intermediate pressure port (49) communicates with the intermediate pressure passage (48). Here, in the first half of the intermediate pressure communication section, from angle θ3 to angle θ4, the pressure in the compression chamber (S) is lower than the set intermediate pressure. Therefore, in the range from angle θ3 to angle θ4, the pressure in the intermediate pressure chamber (43) falls below the set intermediate pressure.

[0063] At angle θ4, the intermediate pressure port (49) is entirely in communication with the intermediate pressure passage (48) (see FIG. 9). At angle θ4, the intermediate pressure port (49) is in communication with the intermediate pressure passage (48). Furthermore, the movable-side oil groove (85) is in communication with the compression chamber (S). From angle θ3 to angle θ4, the amount of oil supplied from the fixed-side oil groove (80) to the compression chamber (S) via the movable-side oil groove (85) increases. Therefore, from angle θ3 to angle θ4, the pressure in the fixed-side oil groove (80) decreases.

[0064] The angle θ5 is before the end of the intermediate pressure communication section, and is the timing when part of the intermediate pressure port (49) is in communication with the intermediate pressure passage (48) (see FIG. 10 ). At the angle θ5, the intermediate pressure port (49) is in communication with the intermediate pressure passage (48). Also, the movable-side oil groove (85) is not in communication with the compression chamber (S). In this way, communication between the movable-side oil groove (85) and the compression chamber (S) ends before the end of the communication section in which the intermediate pressure port (49) is in communication with the intermediate pressure passage (48).

[0065] Furthermore, the amount of oil supplied from the fixed-side oil groove (80) to the compression chamber (S) through the movable-side oil groove (85) decreases from angle θ4 to angle θ5. Therefore, the pressure in the fixed-side oil groove (80) increases from angle θ4 to angle θ5. As a result, the pressure in the fixed-side oil groove (80) becomes high in the angle range after angle θ5.

[0066] The angle θ6 is the timing immediately after the intermediate pressure port (49) leaves the intermediate pressure passage (48) (see FIG. 11). At the angle θ6, the intermediate pressure port (49) does not communicate with the intermediate pressure passage (48). In addition, the movable-side oil groove (85) does not communicate with the compression chamber (S). At the angle θ6, the pressure in the intermediate pressure chamber (43) becomes higher than the set intermediate pressure. Thereafter, from the angle θ6 to the angle θ7, the pressure decreases to the set intermediate pressure.

[0067] As described above, the pressure in the intermediate pressure chamber (43) increases in the latter half of the intermediate pressure communication section in the angular range in which the movable scroll (70) orbits, i.e., from angle θ4 to angle θ6, and therefore the upward pressing force applied to the movable scroll (70) increases from angle θ4 to angle θ6.

[0068] On the other hand, the pressure in the fixed-side oil groove (80) increases from angle θ4 to angle θ5, and therefore the downward pushing force applied to the movable scroll (70) increases from angle θ4 to angle θ5. The pressure in the fixed-side oil groove (80) is approximately constant from angle θ5 to angle θ6.

[0069] As a result, as shown in Figure 12, the timing at which the pressing force pressing the movable scroll (70) toward the fixed scroll (60) increases due to pressure fluctuations in the intermediate pressure chamber (43) can be made to coincide with the timing at which the pushing force pushing the movable scroll (70) away from the fixed scroll (60) increases due to pressure fluctuations in the fixed side oil groove (80), thereby suppressing an increase in thrust surface pressure.

[0070] It is preferable that the movable oil groove (85) and the compression chamber (S) communicate with each other over an angle range of 50% or more of the intermediate pressure communication section. In the example shown in Fig. 6, it is preferable that the angle range from angle θ3 to angle θ5, which is the section where the movable oil groove (85) and the compression chamber (S) communicate with each other, is set to 50% or more of the angle range from angle θ2 to angle θ6, which is the section where the intermediate pressure port (49) and the intermediate pressure passage (48) communicate with each other.

[0071] In addition, it is preferable to set the angle θ5 at which the communication state between the movable-side oil groove (85) and the compression chamber (S) ends, based on the angle θ6 before the end of the communication section in which the intermediate pressure port (49) communicates with the intermediate pressure passage (48), to an angle range greater than 0° before the end of communication and not greater than 30°.

[0072] In addition, it is preferable to set the angle θ3 at which the communication state between the movable-side oil groove (85) and the compression chamber (S) starts, in an angle range of 0° or more and 10° or less after the start of communication, based on the angle θ2 after the start of the communication section in which the intermediate pressure port (49) communicates with the intermediate pressure passage (48).

[0073] Below, as a comparative example, a case will be described with reference to Figure 13 where, during the orbital movement of the movable scroll (70), a section in which the movable side oil groove (85) communicates with the compression chamber (S) and the pushing force due to the pressure of the fixed side oil groove (80) decreases coincides with a section in the latter half of the intermediate pressure communication section in which the pressure in the intermediate pressure chamber (43) increases and the pushing force increases.

[0074] 13, the angle θ1' is the timing at which the space outside the movable scroll (70) is completely closed off. At the angle θ1, the intermediate pressure port (49) does not communicate with the intermediate pressure passage (48). In addition, the movable oil groove (85) does not communicate with the compression chamber (S).

[0075] The angle θ2' is the timing immediately before the intermediate pressure port (49) communicates with the intermediate pressure passage (48). At the angle θ2', the intermediate pressure port (49) does not communicate with the intermediate pressure passage (48). In addition, the movable-side oil groove (85) does not communicate with the compression chamber (S). From the angle θ2' to the angle θ3', the intermediate pressure port (49) communicates with the intermediate pressure passage (48).

[0076] The angle θ3' is the timing when the entire intermediate pressure port (49) communicates with the intermediate pressure passage (48). At the angle θ3', the intermediate pressure port (49) communicates with the intermediate pressure passage (48). In addition, the movable-side oil groove (85) does not communicate with the compression chamber (S).

[0077] The angle θ4' is the timing immediately before the movable-side oil groove (85) communicates with the compression chamber (S). At the angle θ4', the intermediate pressure port (49) communicates with the intermediate pressure passage (48). Also, the movable-side oil groove (85) does not communicate with the compression chamber (S). From the angle θ4' to the angle θ5', the movable-side oil groove (85) communicates with the compression chamber (S). At this time, the amount of oil supplied from the fixed-side oil groove (80) through the movable-side oil groove (85) to the compression chamber (S) increases. Therefore, the pressure in the fixed-side oil groove (80) decreases from the angle θ4' to the angle θ5'.

[0078] The angle θ5' is the timing immediately after the intermediate pressure port (49) leaves the intermediate pressure passage (48). At the angle θ5', the intermediate pressure port (49) does not communicate with the intermediate pressure passage (48). In addition, the movable-side oil groove (85) communicates with the compression chamber (S). At the angle θ5', the pressure in the intermediate pressure chamber (43) becomes higher than the set intermediate pressure. Thereafter, from the angle θ5' to the angle θ7', the pressure decreases to the set intermediate pressure.

[0079] The angle θ6' is the timing when communication between the movable oil groove (85) and the compression chamber (S) ends. At the angle θ6', the intermediate pressure port (49) is not in communication with the intermediate pressure passage (48). In addition, the movable oil groove (85) is not in communication with the compression chamber (S).

[0080] In this manner, in the comparative example, the pressure in the intermediate pressure chamber (43) increases from the angle θ3' to the angle θ5', and therefore the upward pressing force applied to the movable scroll (70) increases from the angle θ3' to the angle θ5'.

[0081] On the other hand, the pressure in the fixed oil groove (80) decreases from the angle θ4' to the angle θ5', and therefore the downward pushing force applied to the movable scroll (70) decreases from the angle θ4' to the angle θ5'.

[0082] As a result, the section in which the movable-side oil groove (85) communicates with the compression chamber (S) and the pushing force due to the pressure in the fixed-side oil groove (80) decreases coincides with the section in the latter half of the intermediate pressure communication section in which the pressure in the intermediate pressure chamber (43) increases and the pushing force increases, causing a local increase in thrust surface pressure, which may deteriorate the sliding condition (see Figure 14).

[0083] In contrast, in the scroll compressor (10) of this embodiment, the timing of the pressure fluctuations in the intermediate pressure chamber (43) and the timing of the pressure fluctuations in the fixed side oil groove (80) are appropriately set to suppress an increase in thrust surface pressure.

[0084] -Effects of the embodiment- According to the features of this embodiment, the timing at which the pressing force pressing the movable scroll (70) toward the fixed scroll (60) increases due to pressure fluctuations in the intermediate pressure chamber (43) and the timing at which the pushing force pushing the movable scroll (70) away from the fixed scroll (60) increases due to pressure fluctuations in the fixed side oil groove (80) can be made to coincide, thereby suppressing an increase in thrust surface pressure.

[0085] According to the features of this embodiment, the communication state between the movable side oil groove (85) and the compression chamber (S) begins after the start of the communication section in which the intermediate pressure port (49) is connected to the intermediate pressure passage (48), so that the increase in thrust surface pressure can be suppressed at an appropriate timing.

[0086] According to the feature of this embodiment, it is possible to suppress an increase in thrust surface pressure in a predetermined angular range in the communication section.

[0087] According to the feature of this embodiment, it is possible to suppress an increase in thrust surface pressure in a predetermined angle range before the end of communication.

[0088] According to the feature of this embodiment, it is possible to suppress an increase in thrust surface pressure in a predetermined angle range after the start of communication.

[0089] According to a feature of the present embodiment, a scroll compressor (10) and a refrigerant circuit (1a) through which the refrigerant compressed by the scroll compressor (10) flows can be provided. This makes it possible to provide a refrigeration system including the scroll compressor (10) and the refrigerant circuit (1a).

[0090] Other Embodiments The above embodiment may be configured as follows.

[0091] In this embodiment, the thickness of the movable end plate (71) in the movable scroll (70) at the portion where the movable oil groove (85) is formed is not specifically described, but, for example, the thickness of the movable end plate (71) at the portion where the movable oil groove (85) is formed may be configured to be smaller than the thickness of the other portions. This allows the portion of the movable end plate (71) surrounding the movable oil groove (85) to elastically deform, thereby suppressing an increase in thrust surface pressure.

[0092] Although the embodiments and modifications have been described above, it will be understood that various modifications of form and details are possible without departing from the spirit and scope of the claims. In addition, the elements of the above embodiments, modifications, and other embodiments may be appropriately combined or substituted. In addition, the descriptions "first," "second," "third," etc. in the specification and claims are used to distinguish the words to which these descriptions are attached, and do not limit the number or order of the words. [Industrial Applicability]

[0093] INDUSTRIAL APPLICABILITY As described above, the present disclosure is useful for scroll compressors and refrigeration systems. [Explanation of symbols]

[0094] 1 Refrigeration equipment 1a Refrigerant circuit 10 Scroll Compressor 43 Intermediate pressure chamber 48 Intermediate pressure passage 49 Intermediate pressure port 60 Fixed Scroll 61 Fixed side head plate 62 Fixed side wrap 70 Movable Scroll 71 Movable side mirror plate 72 Movable side wrap 80 Fixed side oil groove 85 Movable side oil groove S Compression chamber

Claims

1. A scroll compressor comprising: a fixed scroll (60) having a fixed side wrap (62) and a fixed side end plate (61); and a movable scroll (70) having a movable side wrap (72) and a movable side end plate (71), in which a compression chamber (S) is formed by meshing the fixed side wrap (62) and the movable side wrap (72), the fixed-side end plate (61) is provided with a fixed-side oil groove (80) formed on a surface facing the movable-side end plate (71), and an intermediate pressure passage (48) communicating with a space in the compression chamber (S) through which an intermediate-pressure refrigerant flows, the intermediate-pressure refrigerant having a pressure higher than that of the suction refrigerant and lower than that of the discharged refrigerant, The movable-side end plate (71) is provided with a movable-side oil groove (85) formed on a surface facing the fixed-side end plate (61), and an intermediate pressure port (49) communicating with an intermediate pressure chamber (43) provided on the movable-side end plate (71) on the opposite side to the fixed-side end plate (61), The intermediate pressure port (49) overlaps with the intermediate pressure passage (48) in a predetermined angular range during orbital movement of the movable scroll (70) as viewed in the axial direction, The movable oil groove (85) communicates with the compression chamber (S) in a predetermined angular range during orbital movement of the movable scroll (70) as viewed in the axial direction, The communication state between the movable-side oil groove (85) and the compression chamber (S) ends before the end of a communication section in which the intermediate pressure port (49) communicates with the intermediate pressure passage (48). Scroll compressor.

2. The scroll compressor according to claim 1, After the start of the communication section in which the intermediate pressure port (49) communicates with the intermediate pressure passage (48), a communication state between the movable oil groove (85) and the compression chamber (S) begins. Scroll compressor.

3. The scroll compressor according to claim 1 or 2, The movable oil groove (85) and the compression chamber (S) communicate with each other in an angle range of 50% or more in the communication section. Scroll compressor.

4. The scroll compressor according to claim 1 or 2, The communication state between the movable oil groove (85) and the compression chamber (S) ends in an angle range greater than 0° and equal to or less than 30° before the end of communication. Scroll compressor.

5. The scroll compressor according to claim 2, In an angle range of 0° or more and 10° or less after the start of communication, a state of communication between the movable oil groove (85) and the compression chamber (S) begins. Scroll compressor.

6. A scroll compressor (10) according to claim 1 or 2; a refrigerant circuit (1a) through which the refrigerant compressed by the scroll compressor (10) flows. Refrigeration equipment.

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