Rotary compressor and refrigeration cycle system

Abstract

Reduce the oil pickup rate. 【Solution means】The refrigerant is a single refrigerant composed of a hydrocarbon refrigerant or a mixed refrigerant containing the hydrocarbon refrigerant. The displacement volume of the compression mechanism (40) is Vc [cc], the density of the refrigerant at 1.9 Mpa and 75 °C is Dg [g / cm 3 , the rotational speed of the rotating shaft (30) is N [rps], the volume of the primary space (S1) is V1 [cc], the volume of the secondary space (S2) is V2 [cc], the height of the primary space (S1) is H1 [cm], the height of the secondary space (S2) is H2 [cm], and the density of the refrigeration oil at 15 °C is Do [g / cm 3 . The dissolved viscosity of the refrigeration oil existing below the height position of the suction port (71a) is defined as η [mPa·S]. The rotary compressor satisfies the relational expression of N≧100 [rps] and ((8.19×10 -8 ×Vc×Dg + 0.000327)×Vc 3.657 ×N 3.126 ) / (V1×V2×H1 1.867 ×H2 1.556 ×Do×η)≦1.0.

Description

[Technical Field]

[0001] This disclosure relates to rotary compressors and refrigeration cycle devices. A rotary compressor is a compressor that compresses gas in a compression chamber formed in a cylinder by eccentrically rotating a roller within the cylinder. Rotary compressors generally have vanes for partitioning the compression chamber. Rotary compressors include so-called swing type, in which vanes formed integrally with the rollers oscillate with the eccentric rotation of the rollers; so-called rolling piston type, in which vanes separate from the rollers abut the rollers while the rollers rotate eccentrically; and so-called hinge vane type, in which the tips of the vanes are rotatably fitted into recesses on the outer surface of the rollers while the rollers rotate eccentrically. [Background technology]

[0002] Patent Document 1 discloses a refrigeration cycle device. The refrigeration cycle device has a refrigerant circuit. The refrigerant circuit has a rotary compressor, a heat sink, an expansion valve, and an evaporator. When the rotary compressor is operated, the refrigerant in the refrigerant circuit circulates and the refrigeration cycle is performed.

[0003] In a rotary compressor, the refrigerant compressed by the compression mechanism flows out through the space inside the casing to the refrigerant circuit via the discharge pipe. In this way, the inside of the casing is filled with high-pressure refrigerant.

[0004] An oil reservoir is formed at the bottom of the casing to hold refrigeration oil. The refrigeration oil is used to lubricate the sliding parts of the rotary compressor. The refrigeration oil in the reservoir is drawn in through the intake port of the oil supply pump and supplied to the sliding parts of the compression mechanism and other components through the oil supply passage in the rotating shaft. [Prior art documents] [Patent Documents]

[0005] [Patent Document 1] Japanese Patent Publication No. 2023-162986 [Overview of the project] [Problems that the invention aims to solve]

[0006] Hydrocarbon refrigerants, such as propane, are used as refrigerants in the refrigerant circuits of refrigeration cycle systems. Hydrocarbon refrigerants are natural refrigerants and have an extremely low global warming potential. On the other hand, hydrocarbon refrigerants generally have a molecular structure similar to that of refrigerant oil and have the characteristic of dissolving easily in refrigerant oil. When the refrigerant dissolves in the refrigerant oil, the solubility viscosity of the refrigerant oil decreases, and the viscous resistance of the refrigerant oil decreases. As a result, the refrigerant oil in the casing is more likely to leak out of the discharge pipe into the refrigerant circuit along with the refrigerant, which can increase the oil rise rate (the proportion of refrigerant oil contained in the fluid leaking out of the discharge pipe).

[0007] The purpose of this disclosure is to reduce the rate of oil consumption. [Means for solving the problem]

[0008] The first embodiment relates to a rotary compressor. The rotary compressor comprises an electric motor (25), a rotating shaft (30) connected to the electric motor (25), a compression mechanism (40) positioned below the electric motor (25) and driven by the rotating shaft (30) to compress the refrigerant, a casing (21) housing the electric motor (25), the rotating shaft (30), and the compression mechanism (40) and filled with high-pressure refrigerant discharged from the compression mechanism (40), and a lubrication mechanism (70) having a suction port (71a) for drawing in refrigerant oil accumulated at the bottom of the casing (21) and supplying the refrigerant oil to the sliding parts. The compression mechanism (40) includes annular cylinders (51A, 51B), annular rollers (52A, 52B) that rotate eccentrically within the cylinders (51A, 51B), and vanes (53A, 53B) for forming a compression chamber within the cylinders (51A, 51B). The internal space (S) of the casing (21) includes a primary space (S1) between the compression mechanism (40) and the electric motor (25), and a secondary space (S2) above the electric motor (25). A discharge pipe (24) communicating with the secondary space (S2) is connected to the casing (21). The refrigerant is a single refrigerant consisting of a hydrocarbon refrigerant, or a mixed refrigerant containing a hydrocarbon refrigerant. The displacement volume of the compression mechanism (40) is Vc [cc], and the density of the refrigerant at 1.9 MPa and 75°C is Dg [g / cm³]. 3 ], the rotational speed of the rotating shaft (30) is N [rps], the volume of the primary space (S1) is V1 [cc], the volume of the secondary space (S2) is V2 [cc], the height of the primary space (S1) is H1 [cm], the height of the secondary space (S2) is H2 [cm], and the density of the refrigerant oil at 15°C is Do [g / cm³] 3 The soluble viscosity of the refrigerant oil present below the height of the suction port (71a) is defined as η [mPa·S]. The rotary compressor has N ≥ 100 [rps] and ((8.19 × 10 -8 ×Vc×Dg+0.000327)×Vc 3.657 ×N 3.126 ) / (V1×V2×H1 1.867 ×H2 1.556 The relationship ×Do ​​× η) ≤ 1.0 is satisfied.

[0009] As a result of verification, it was confirmed that even during operation where the rotational speed N is 100 [rps] or more, by satisfying the above relational expression, the oil rise rate α can be made 1.0% or less. Therefore, in the first aspect, during operation where the rotational speed N of the rotating shaft (30) is 100 or more, the oil rise rate α can be made 1.0% or less.

[0010] In a second aspect, in the first aspect, when the total height of the casing (21) is defined as Hc, H2 / Hc ≤ 0.25.

[0011] In the second aspect, by setting H2 / Hc ≤ 0.25, the volume of the secondary space (S2) becomes relatively small, and the amount of refrigerant retained in the secondary space (S2) can be reduced. Therefore, the amount of refrigerant used in the refrigeration cycle of the refrigerant circuit (10) can be ensured.

[0012] In a third aspect, in the first or second aspect, when the total height of the casing (21) is defined as H, 0.2 ≤ H2 / Hc.

[0013] In the third aspect, it is possible to suppress the height H2 of the secondary space (S2) from becoming excessively small. As a result, since oil can be separated from the refrigerant in the secondary space (S2), the oil rise rate can be reduced.

[0014] In a fourth aspect, in any one of the first to third aspects, the refrigeration oil contains any one of polyalkylene glycol, polyvinyl ether, or polyol ester.

[0015] In the fourth aspect, the refrigeration oil contains polyalkylene glycol, polyvinyl ether, or polyol ester. These refrigeration oils are relatively insoluble in hydrocarbon refrigerants. Therefore, it is possible to suppress an increase in the oil rise rate due to the hydrocarbon refrigerant dissolving in the refrigeration oil.

[0016] In a fifth aspect, in any one of the first to fourth aspects, the density Do [g / cm 3 of the refrigerant is 37 [g / cm 3is above 44 [g / cm 3 and below.

[0017] In the fifth aspect, since the density Do of the refrigerant is relatively small, the refrigerant circulation amount of the refrigeration cycle becomes small. As a result, the oil rising rate can be reduced.

[0018] In the sixth aspect, in any one of the first to fifth aspects, the refrigeration oil contains at least one of an extreme pressure additive of phosphoric esters, an antioxidant, and an acid scavenger.

[0019] In the seventh aspect, in any one of the first to sixth aspects, the refrigeration oil contains an antioxidant or an acid scavenger in an amount of 0.1% by weight or more and 0.5% by weight or less.

[0020] In the seventh aspect, since the antioxidant or the acid scavenger is 0.5% by weight or less based on the weight of the refrigeration oil, it is possible to suppress the excessive decrease in the dissolved viscosity of the refrigeration oil due to the increase in the content of the antioxidant or the acid scavenger. As a result, the oil rising rate can be reduced.

[0021] In the eighth aspect, in any one of the first to seventh aspects, the refrigeration oil contains an extreme pressure additive in an amount of 1.0% by weight or more and 5.0% by weight or less.

[0022] In the eighth aspect, since the extreme pressure additive is 5.0% by weight or less based on the weight of the refrigeration oil, it is possible to suppress the excessive decrease in the dissolved viscosity of the refrigeration oil due to the increase in the content of the extreme pressure additive. As a result, the oil rising rate can be reduced.

[0023] In the ninth aspect, in any one of the first to eighth aspects, the molecular weight of the refrigeration oil is 1000 or more and 1800 or less.

[0024] In the ninth aspect, by setting the molecular weight of the refrigeration oil to be 1000 or more and 1800 or less, it is possible to suppress the hydrocarbon refrigerant from dissolving into the refrigeration oil. As a result, the oil rising rate can be reduced.

[0025] The tenth embodiment relates to a refrigeration cycle device. The refrigeration cycle device has one of the first to ninth compressors (20) and a refrigerant circuit (10) through which a hydrocarbon refrigerant circulates to perform a refrigeration cycle. [Brief explanation of the drawing]

[0026] [Figure 1] Figure 1 is a piping diagram of the refrigeration cycle system. [Figure 2] Figure 2 is a longitudinal cross-sectional view of the compressor. [Figure 3] Figure 3 is a magnified longitudinal cross-sectional view of the main part of the compressor. [Figure 4] Figure 4 is a cross-sectional view of the first compression element. [Figure 5] Figure 5 is a cross-sectional view of the second compression element. [Figure 6] Figure 6 is a magnified longitudinal cross-sectional view of a portion of the compressor to illustrate the primary and secondary spaces. [Modes for carrying out the invention]

[0027] Embodiments of this disclosure will be described in detail below with reference to the drawings. This disclosure is not limited to the embodiments shown below, and various modifications are possible without departing from the technical idea of ​​this disclosure. Since the drawings are for conceptual illustration of this disclosure, dimensions, ratios, or numbers may be exaggerated or simplified as necessary for ease of understanding.

[0028] (1) Overall configuration of the refrigeration cycle system The refrigeration cycle system of this disclosure is applicable to a stationary air conditioning system (1). As shown in Figure 1, the air conditioning system (1) is a paired system having one outdoor unit (OU) installed outdoors and one indoor unit (IU) installed indoors. The outdoor unit (OU) and the indoor unit (IU) are connected to each other via two connecting pipes.

[0029] The air conditioning system (1) has a refrigerant circuit (10). The refrigerant circuit (10) is filled with refrigerant. The refrigerant circuit (10) performs a refrigeration cycle by circulating the refrigerant. The refrigerant circuit (10) has a compressor (20), an outdoor heat exchanger (11), an expansion valve (12), and an indoor heat exchanger (13). The refrigerant circuit (10) further has a four-way switching valve (14) for switching between a cooling cycle and a heating cycle. The compressor (20), the outdoor heat exchanger (11), and the expansion valve (12) are installed in the outdoor unit (OU), and the indoor heat exchanger (13) is installed in the indoor unit (IU). The expansion valve (12) may also be installed in the indoor unit (IU).

[0030] The compressor (20) draws in the low-pressure refrigerant from the refrigerant circuit (10) and compresses it. The compressor (20) discharges the compressed refrigerant as high-pressure refrigerant back into the refrigerant circuit (10). The outdoor heat exchanger (11) is a fin-and-tube type heat exchanger. The outdoor heat exchanger exchanges heat between the refrigerant in the refrigerant circuit (10) and the outdoor air transported by the outdoor fan (15). The expansion valve (12) is an example of a pressure reduction mechanism for reducing the pressure of the refrigerant. The expansion valve (12) is an electronically controlled expansion valve with an adjustable opening. The indoor heat exchanger (13) is a fin-and-tube type heat exchanger. The indoor heat exchanger exchanges heat between the refrigerant in the refrigerant circuit (10) and the outdoor air transported by the indoor fan (16).

[0031] The four-way directional control valve (14) has a first port (P1), a second port (P2), a third port (P3), and a fourth port (P4). The four-way directional control valve (14) switches between a first state, shown by the solid line in Figure 1, and a second state, shown by the dashed line in Figure 1. In the first state, the four-way directional control valve (14) connects the first port (P1) and the second port (P2) and simultaneously connects the third port (P3) and the fourth port (P4). When the four-way directional control valve (14) is in the first state, the compressor (20) is operated, and a cooling cycle is performed in which the outdoor heat exchanger (11) functions as a heat radiator (condenser) and the indoor heat exchanger (13) functions as an evaporator. In the second state, the four-way switching valve (14) connects the first port (P1) and the third port (P3) while simultaneously connecting the second port (P2) and the fourth port (P4). When the four-way switching valve (14) is in the second state, the compressor (20) is operated, and a heating cycle is performed in which the indoor heat exchanger (13) functions as a radiator (condenser) and the outdoor heat exchanger (11) functions as an evaporator.

[0032] (2) Compressor The configuration of the compressor (20) will be explained with reference to Figures 2 to 6. In the following explanation, the terms "up" and "down" refer to the directions indicated by the arrows in Figure 2. In the following explanation, "axial direction" means the direction in which the axis (A) of the rotating shaft (30) shown in Figure 2 extends, "radial direction" means the direction that passes through the axis (A) of the rotating shaft (30) and is perpendicular to the axis (A), and "circumferential direction" means the direction of rotation of the rotating shaft (30).

[0033] The compressor (20) is a rotary compressor. The rotary compressor in this embodiment is a so-called swing type in which vanes (53A, 53B) formed integrally with the rollers (52A, 52B) swing in accordance with the eccentric rotation of the rollers (52A, 52B).

[0034] The compressor (20) has a casing (21) and a plurality of component parts housed in the casing (21). The plurality of component parts include an electric motor (25), a rotating shaft (30), a compression mechanism (40), and a lubrication mechanism (70). The electric motor (25) is the drive source for the compression mechanism (40). The rotating shaft (30) is connected to the electric motor (25). Bearings (44, 45) rotatably support the rotating shaft (30). The compression mechanism (40) compresses the refrigerant by being rotationally driven by the rotating shaft (30). The lubrication mechanism (70) supplies refrigerant oil, which is a lubricating oil, to a plurality of sliding parts.

[0035] (2-1) Casing The casing (21) is a hollow, sealed container. An internal space (S) is formed inside the casing (21). The casing (21) is formed to be elongated vertically, extending axially, or more precisely, vertically. The casing (21) has a vertically extending cylindrical body (21a), an upper lid (21b) that closes the upper end of the body (21a), and a lower lid (21c) that closes the lower end of the body (21a). The lower lid (21c) constitutes the bottom of the casing (21).

[0036] The internal space (S) of the casing (21) is filled with discharged refrigerant discharged from the compression mechanism (40). That is, the compressor (20) is a so-called high-pressure dome type. The internal space (S) of the casing (21) includes a primary space (S1) between the compression mechanism (40) and the electric motor (25), and a secondary space (S2) above the electric motor (25).

[0037] An oil reservoir (35) for storing refrigerant oil is formed at the bottom of the casing (21). In the oil reservoir (35), the oil level of the refrigerant oil changes according to the operating conditions of the compressor (20) and the air conditioning unit (1).

[0038] (2-2) First inhalation tube, second inhalation tube, and discharge tube The casing (21) is connected to a first suction pipe (23A), a second suction pipe (23B), and a discharge pipe (24). The first suction pipe (23A) and the second suction pipe (23B) pass radially through the body (21a). The first suction pipe (23A) and the second suction pipe (23B) are connected to the low-pressure line of the refrigerant circuit (10). The discharge pipe (24) passes axially through the upper cover (21b). The discharge pipe (24) is connected to the high-pressure line of the refrigerant circuit (10).

[0039] (2-3) Electric motor The electric motor (25) is located in the upper part of the internal space (S). The electric motor (25) has a stator (26) and a rotor (27). The stator (26) is fixed to the inner circumferential surface of the body (21a). The stator (26) is formed in a cylindrical shape when viewed in a cross section perpendicular to the axial direction (horizontal cross section). The rotor (27) is positioned radially inward of the stator (26). The rotor (27) is fixed to the outer circumferential surface of the rotating shaft (30). The electric motor (25) is configured so that its rotational speed can be adjusted by an inverter device. In other words, the electric motor (25) is an inverter-type electric motor with a variable operating frequency.

[0040] (2-4) Rotation axis The rotating shaft (30) is located at the radial center of the internal space (S). The rotating shaft (30) extends vertically. The rotating shaft (30) has a shaft body (31) and a first eccentric portion (32A) and a second eccentric portion (32B) that are radially eccentric from the axis (A) of the shaft body (31). The rotor (27) of the electric motor (25) is connected to the upper part of the shaft body (31). The first eccentric portion (32A) and the second eccentric portion (32B) are formed at the lower part of the shaft body (31). The first eccentric portion (32A) is located above the second eccentric portion (32B). The direction in which the first eccentric portion (32A) is eccentric from the axis (A) and the direction in which the second eccentric portion (32B) is eccentric from the axis are offset by 180° from each other in the circumferential direction.

[0041] (2-5) Overall configuration of the compression mechanism The compression mechanism (40) is located below the electric motor (25). The compression mechanism (40) has, in order from top to bottom, a front head (41), a first cylinder (51A), a middle plate (42), a second cylinder (51B), and a rear head (43). These components are fastened to each other by bolts that extend axially.

[0042] The compression mechanism (40) of this embodiment comprises a first compression element (C1) and a second compression element (C2). The first compression element (C1) has a first roller (52A) and a first vane (53A). The second compression element (C2) has a second roller (52B) and a second vane (53B). In the compression mechanism (40) of this embodiment, the rollers (52A, 52B) and vanes (53A, 53B) are integrally configured, and the vanes (53A, 53B) swing in accordance with the eccentric rotation of the rollers (52A, 52B).

[0043] A first cylinder chamber (54A) is formed inside the first cylinder (51A). The first cylinder chamber (54A) penetrates the first cylinder (51A) in the axial direction. A second cylinder chamber (54B) is formed inside the second cylinder (51B). The second cylinder chamber (54B) penetrates the second cylinder (51B) in the axial direction.

[0044] (2-5-1) Closure member The front head (41), middle plate (42), and rear head (43) are examples of occluding members that axially close off the cylinder chambers (54A, 54B). The front head (41) has a first occluding portion (41a) which is a flat plate with a slightly thicker wall in the axial direction, and an upper bearing portion (41b) which extends upward from the radial center of the first occluding portion (41a).

[0045] The lower surface of the first closure portion (41a) closes the upper opening surface of the first cylinder chamber (54A). As shown in Figure 4, the first closure portion (41a) has a first discharge port (55A) that communicates with the high-pressure chamber (compression chamber) of the first cylinder chamber (54A). The first discharge port (55A) is opened and closed by a first discharge valve (not shown).

[0046] The upper bearing portion (41b) is formed in a cylindrical shape that extends axially along the rotating shaft (30). The rotating shaft (30) passes through the interior of the upper bearing portion (41b). A first bearing (44) is formed on the inner circumferential surface of the upper bearing portion (41b). The first bearing (44) rotatably supports the main shaft portion of the rotating shaft (30). The first bearing (44) is composed of a sliding bearing, more precisely a journal bearing.

[0047] The middle plate (42) is positioned between the first cylinder (51A) and the second cylinder (51B). The middle plate (42) is formed in an annular shape. The rotating shaft (30) passes through the interior of the middle plate (42). The upper surface of the middle plate (42) closes the lower opening of the first cylinder chamber (54A). The lower surface of the middle plate (42) closes the upper opening of the second cylinder chamber (54B).

[0048] The rear head (43) has a second closure portion (43a) which is a flat plate with a slightly thicker wall in the axial direction, and a lower bearing portion (43b) which extends downward from the radial center of the second closure portion (43a). The upper surface of the second closure portion (43a) closes the lower opening surface of the second cylinder chamber (54B). As shown in Figure 5, the second closure portion (43a) has a second discharge port (55B) which communicates with the high-pressure chamber (compression chamber) of the second cylinder chamber (54B). The second discharge port (55B) is opened and closed by a second discharge valve (not shown).

[0049] The lower bearing portion (43b) is formed in a cylindrical shape that extends axially along the rotating shaft (30). The rotating shaft (30) passes through the interior of the lower bearing portion (43b). A second bearing (45) is formed on the inner circumferential surface of the lower bearing portion (43b). The second bearing (45) rotatably supports the sub-shaft portion of the rotating shaft (30). The second bearing (45) is composed of a sliding bearing, more precisely a journal bearing.

[0050] (2-5-2) Details of the first compression element The first compression element (C1) shown in Figure 4 includes a first eccentric portion (32A), a first cylinder (51A), a first roller (52A), a first vane (53A), and a pair of first bushes (56A).

[0051] The first cylinder (51A) is an annular member that is slightly thicker in the axial direction. Inside the first cylinder (51A), a first cylinder chamber (54A) is formed. The first cylinder chamber (54A) is formed in a circular shape when viewed in the axial direction. The first cylinder (51A) has a first intake passage (57A) and a first bush groove (58A) formed therein. The first intake passage (57A) penetrates the first cylinder (51A) radially. The first intake passage (57A) communicates with the first intake pipe (23A).

[0052] The first roller (52A) is positioned in the first cylinder chamber (54A). The first roller (52A) is formed in an annular shape when viewed in the axial direction. The first eccentric part (32A) is fitted inside the first roller (52A). The inner circumferential surface of the first roller (52A) and the outer circumferential surface of the first eccentric part (32A) slide relative to each other. The first eccentric part (32A) causes the first roller (52A) to rotate eccentrically. The first roller (52A) rotates eccentrically along the inner circumferential surface of the first cylinder chamber (54A), forming a seal between itself and the inner circumferential surface of the first cylinder chamber (54A).

[0053] The first bush groove (58A) is formed on the top dead center side (upper side in Figure 3) of the first cylinder (51A). The first bush groove (58A) is formed in a circular shape when viewed in the axial direction. A pair of first bushes (56A) fit into the first bush groove (58A). Each pair of first bushes (56A) has an arc-shaped portion that follows the inner surface of the first bush groove (58A) and flat portions that are continuous with both ends of the arc-shaped portion. The pair of first bushes (56A) are arranged in the first bush groove (58A) so that their respective flat portions face each other. The flat portions of the pair of first bushes (56A) hold the first vane (53A). The pair of first bushes (56A) are configured to swing along the inner surface of the first bush groove (58A). The first vane (53A) is configured to reciprocate radially between the pair of first bushes (56A).

[0054] The first vane (53A) constitutes a partition member that divides the first cylinder chamber (54A) into a low-pressure chamber (L) and a high-pressure chamber (H). The radially inner portion of the first vane (53A) is continuous with the outer surface of the first roller (52A). The low-pressure chamber (L) of the first cylinder chamber (54A) communicates with the first suction passage (57A) and constitutes a suction chamber into which low-pressure refrigerant flows. The high-pressure chamber (H) of the first cylinder chamber (54A) is isolated from the first suction passage (57A) and constitutes a compression chamber for compressing the refrigerant.

[0055] (2-5-3) Details of the second compression element The second compression element (C2) shown in Figure 5 has a second eccentric portion (32B), a second cylinder (51B), a second roller (52B), a second vane (53B), and a pair of second bushes (56B). The basic structure of the second eccentric portion (32B), the second cylinder (51B), the second roller (52B), the second vane (53B), and the pair of second bushes (56B) is the same as that of the first eccentric portion (32A), the first cylinder (51A), the first roller (52A), the first vane (53A), and the pair of first bushes (56A), respectively, so a detailed explanation is omitted. The second cylinder (51B) has a second cylinder chamber (54B), a second intake passage (57B), and a second bush groove (58B). The basic structure of the second cylinder chamber (54B), the second intake passage (57B), and the second bush groove (58B) is the same as that of the first cylinder chamber (54A), the first intake passage (57A), and the first bush groove (58A), respectively, so a detailed explanation is omitted. The second intake passage (57B) is connected to the second intake pipe (23B). The first roller (52A) and the second roller (52B) are 180° out of phase with respect to each other during eccentric rotation.

[0056] (2-6) Fueling mechanism The lubrication mechanism (70) shown in Figure 3 supplies refrigerant oil from the oil reservoir (35) to multiple sliding parts. The lubrication mechanism (70) is located at the bottom of the rotating shaft (30). The lubrication mechanism (70) includes a lubrication pump (71) and a lubrication passage (72).

[0057] The oil supply pump (71) is located at the lower end of the rotating shaft (30). The oil supply pump (71) is positioned lower than the oil level in the oil reservoir (35). The oil supply pump (71) transports the refrigerant oil from the oil reservoir (35). The oil supply pump (71) has a suction port (71a) for drawing in the refrigerant oil from the oil reservoir (35). The suction port (71a) opens downward toward the bottom of the casing (21). The oil supply pump (71) is a differential pressure type, centrifugal type, or positive displacement type pump.

[0058] The oil supply passage (72) is formed inside the rotating shaft (30). The oil supply passage (72) communicates with the discharge side of the oil supply pump (71). The oil supply passage (72) has a main passage (73) that extends vertically through the axis of the rotating shaft (30) and a plurality of branch passages that extend radially from the main passage (73). The plurality of branch passages include, in order from top to bottom, a first branch passage (74a), a second branch passage (74b), a third branch passage (74c), and a fourth branch passage (74d).

[0059] The first branch channel (74a) is located at the same height as the upper bearing (41b). The outlet of the first branch channel (74a) opens toward the first bearing (44). In other words, the first branch channel (74a) opens toward the sliding part between the first bearing (44) and the rotating shaft (30). The second branch channel (74b) is formed in the first eccentric part (32A). The outlet of the second branch channel (74b) opens toward the inner circumferential surface of the first roller (52A). In other words, the second branch channel (74b) opens toward the sliding part between the first roller (52A) and the first eccentric part (32A). The third branch channel (74c) is formed in the second eccentric part (32B). The outlet of the third branch channel (74c) opens toward the inner circumferential surface of the first roller (52A). In other words, the third branch channel (74c) opens toward the sliding part between the second roller (52B) and the second eccentric part (32B). The fourth branch channel (74d) is at the same height as the lower bearing part (43b). The outlet of the fourth branch channel (74d) opens toward the second bearing (45). In other words, the fourth branch channel (74d) opens toward the sliding part between the second bearing (45) and the rotating shaft (30).

[0060] (2-7) Operating procedures When the rotating shaft (30) is rotated by the electric motor (25), the first eccentric part (32A) and the second eccentric part (32B) rotate eccentrically. In the first compression element (C1), as the first roller (52A) rotates eccentrically, low-pressure refrigerant is drawn from the first suction pipe (23A) into the low-pressure chamber (L) of the first cylinder chamber (54A). At the same time, the refrigerant is compressed in the high-pressure chamber (H) of the first cylinder chamber (54A). In the second compression element (C2), as the second roller (52B) rotates eccentrically, low-pressure refrigerant is drawn from the second suction pipe (23B) into the second low-pressure chamber (L) of the first cylinder chamber (54A). At the same time, the refrigerant is compressed in the high-pressure chamber (54B) of the second cylinder chamber (54B).

[0061] When the internal pressure in the compression chamber of the first compression element (C1) rises and the first reed valve opens, high-pressure refrigerant is discharged into the internal space (S) through the first discharge port (55A). When the internal pressure in the compression chamber of the second compression element (C2) rises and the second reed valve opens, high-pressure refrigerant is discharged into the internal space (S) through the second discharge port (55B). The high-pressure refrigerant surrounding the compression mechanism (40) passes above the electric motor (25) and is discharged into the refrigerant circuit (10) via the discharge pipe (24).

[0062] As the rotating shaft (30) rotates, the oil supply pump (71) rotates along with the rotating shaft (30). As a result, the refrigerant oil in the oil reservoir (35) is drawn into the suction port (71a). The oil supply pump (71) sends the refrigerant oil drawn in from the suction port (71a) to each branch channel (74a, 74b, 74c, 74d) via the main channel (73). The refrigerant oil in the first branch channel (74a) is used to lubricate the sliding part of the first bearing (44), the refrigerant oil in the second branch channel (74b) is used to lubricate the sliding part of the first eccentric part (32A), the refrigerant oil in the third branch channel (74c) is used to lubricate the sliding part of the second eccentric part (32B), and the refrigerant oil in the fourth branch channel (74d) is used to lubricate the sliding part of the second bearing (45).

[0063] (3) Refrigerant The refrigerant in this embodiment is a hydrocarbon refrigerant. The hydrocarbon refrigerant in this embodiment is a single refrigerant consisting of propane (R290). Propane has an extremely low global warming potential and is environmentally friendly. On the other hand, hydrocarbon refrigerants such as propane have a molecular structure similar to that of refrigeration oil, and therefore have the characteristic of being easily soluble in refrigeration oil.

[0064] The hydrocarbon refrigerant may be a single refrigerant consisting of isobutane. The refrigerant in the refrigerant circuit (10) may be a mixed refrigerant containing a hydrocarbon refrigerant and at least one other refrigerant. Examples of other refrigerants include HFC (hydrofluorocarbon) refrigerants, HFO (hydrofluoroolefin) refrigerants, and CF3I (trifluoroiodomethane).

[0065] (4) Refrigerating machine oil Next, the refrigerant oil used in the refrigerant circuit (10) will be explained. Here, refrigerant oil refers to a fluid that contains additives such as extreme pressure additives, antioxidants, and acid scavengers, in addition to the components used for lubricating sliding parts (lubricating oil).

[0066] The refrigerant oil used in the refrigerant circuit (10) of this embodiment contains either PAG (polyalkylene glycol), PVE (polyvinyl ether), or POE (polyol ester). The refrigerant oil is mainly composed of PAG, PVE, or POE.

[0067] Hydrocarbon refrigerants such as propane have a molecular structure similar to that of refrigeration oil, and therefore dissolve easily in refrigeration oil. In contrast, PAG, PVE, or POE have relatively low compatibility with hydrocarbon refrigerants. For this reason, using PAG, PVE, or POE as the refrigeration oil can suppress the dissolution of the refrigerant into the oil. The refrigeration oil may also be alkylbenzene or mineral oil.

[0068] The refrigerant oil has the characteristic of separating into two layers when the refrigerant pressure is 1.9 MPa and the temperature of the refrigerant oil is 75°C. Therefore, the refrigerant oil in the oil reservoir (35) separates into two layers when the refrigerant pressure in the casing (21) is 1.9 MPa and the temperature of the refrigerant oil is 75°C.

[0069] Generally, refrigerant oil dissolves uniformly with the refrigerant. However, by using refrigerant oil with low solubility with the refrigerant, a concentration gradient between the refrigerant oil and the refrigerant is created in the oil reservoir (35), resulting in a so-called two-layer separation of the refrigerant oil. The refrigerant oil near the surface of the oil reservoir (35) has a lower density of refrigerant, thus forming a layer with high refrigerant solubility. The refrigerant oil near the bottom of the oil reservoir (35) has a higher density of refrigerant, thus forming a layer with low refrigerant solubility. The dissolution viscosity of the refrigerant oil changes depending on the refrigerant solubility. Therefore, the dissolution viscosity of the refrigerant oil can be ensured by suppressing the refrigerant solubility. When refrigerant and refrigerant oil are mixed, the state in which the refrigerant and refrigerant oil do not dissolve and separate into two layers, or an emulsion state, is called a two-layer separation state.

[0070] The molecular weight of the refrigeration oil is preferably between 1000 and 1800.

[0071] The refrigeration oil contains at least one additive, which is an extreme pressure additive of phosphate esters, an antioxidant, and an acid scavenger.

[0072] As extreme pressure additives of phosphate esters, those containing phosphate esters, phosphite esters, acidic phosphate esters, acidic phosphite esters, and amine salts of acidic phosphite esters can be used.

[0073] As acid scavengers, epoxy compounds such as phenyl glycidyl ether, alkyl glycidyl ether, alkylene glycol glycidyl ether, cyclohexene oxide, α-olefin oxide, and epoxidized soybean oil can be used.

[0074] For antioxidants, phenol-based antioxidants or amine-based antioxidants can be used.

[0075] The refrigeration oil contains 1.0% to 5.0% by weight of extreme pressure additives. The refrigeration oil also contains 0.1% to 0.5% by weight of antioxidants or acid scavengers.

[0076] The refrigerant oil of this embodiment has a surface tension of 0.25 [N / m] or more and 0.40 [N / m] or less at 20°C. The surface tension of the refrigerant oil is measured by a method conforming to JIS K2241.

[0077] (5) Regarding the parameters of the compressor (5-1) Tasks Hydrocarbon refrigerants such as propane have a molecular structure similar to that of refrigeration oil, and therefore dissolve easily in refrigeration oil. When the refrigerant dissolves in the refrigeration oil, the viscosity of the refrigeration oil decreases, and the viscous resistance of the refrigeration oil decreases. As a result, the refrigeration oil in the casing (21) is more likely to leak out of the discharge pipe (24) into the refrigerant circuit (10) along with the refrigerant, which may increase the rate of oil leakage.

[0078] In addition, because hydrocarbon refrigerants are highly flammable, the amount of refrigerant charged into the refrigerant circuit (10) may be limited to account for the risk of refrigerant leakage. However, since hydrocarbon refrigerants dissolve easily in refrigerant oil, a large amount of refrigerant is retained in the internal space (S) of the compressor (20) together with the refrigerant oil. This leads to a problem where the amount of refrigerant used in the refrigeration cycle of the refrigerant circuit (10) tends to be insufficient. This problem of insufficient refrigerant is particularly pronounced in separate-type air conditioning systems (1) where the indoor unit (IU) and the outdoor unit (OU) are separated, as the refrigerant piping length is relatively long.

[0079] (5-2) Overview of the relational expression Therefore, in order to solve these problems, the compressor (20) of this embodiment is configured to satisfy the following parameter relationships.

[0080] The displacement volume of the compression mechanism (40) is Vc [cc], and the density of the refrigerant at 1.9 MPa and 75°C is Dg [g / cm³].3 ], the rotational speed of the rotating shaft (30) is N [rps], the volume of the primary space (S1) is V1 [cc], the volume of the secondary space (S2) is V2 [cc], the height of the primary space (S1) is H1 [cm], the height of the secondary space (S2) is H2 [cm], the total height of the casing (21) is Hc [cm], and the density of the refrigerant oil at 15°C is Do [g / cm³]. 3 The soluble viscosity of the refrigerant oil present at or below the height position h1 of the suction port (71a) is defined as η [mPa·S], and the oil consumption rate of the rotary compressor is defined as α (weight %).

[0081] The compressor (20) of this embodiment satisfies the following equations (1), (2), (3), and (4).

[0082] N≧100...Equation (1) ((8.19 × 10 -8 ×Vc×Dg+0.000327)×Vc 3.657 ×N 3.126 ) / (V1×V2×H1 1.867 ×H2 1.556 ×Do×η)≦α, (α=1.0)···(2) formula H2 / Hc≦0.25···(3) formula 0.2≦H2 / Hc···(4) formula (5-3) Explanation of each parameter The oil leakage rate α is the ratio of the weight Wo of refrigerant oil to the total weight Wt of the fluid flowing out of the discharge pipe (24), expressed as a percentage (α = Wo / Wt × 100).

[0083] As the rotational speed N of the rotating shaft (30) increases, the amount of refrigerant circulating in the refrigerant circuit (10) increases, making it easier for refrigerant oil to leak out of the casing (21) along with the refrigerant. Therefore, as the rotational speed N increases, the oil leakage rate α also increases. In this embodiment, the rotational speed N is 100 [rps] or higher, which is relatively high, so the oil leakage rate tends to increase.

[0084] The displacement volume Vc is the volume of the high-pressure chamber (compression chamber) when the low-pressure chamber (L) is completely closed within the cylinder (51A, 51B) and the high-pressure chamber (compression chamber) is formed, and corresponds to the maximum volume of the compression chamber. The compression mechanism (40) in this embodiment is a two-cylinder type. In this case, the Vc defined here is the sum of the displacement volume Vc-1 of the first cylinder (51A) and the displacement volume Vc-2 of the second cylinder (51B). If the number of cylinders is n, and the displacement volumes of each cylinder are Vc-n, Vc-n+1, ​​..., then the displacement volume Vc is the sum of these displacement volumes Vc-n, Vc-n+1, ​​...

[0085] As the displacement volume Vc increases, the refrigerant circulation rate in the refrigerant circuit (10) increases, making it easier for refrigerant oil to leak out of the casing (21) along with the refrigerant. Therefore, as the displacement volume Vc increases, the oil leakage rate α also increases.

[0086] As the rotational speed N of the rotating shaft (30) increases, the amount of refrigerant circulating in the refrigerant circuit (10) increases, making it easier for refrigerant oil to leak out of the casing (21) along with the refrigerant. Therefore, as the rotational speed N increases, the oil leakage rate α increases. The rotational speed N is preferably 120 [rps] or higher, and more preferably 150 [rps] or higher. The rotational speed N may also be greater than or equal to the maximum rotational speed Nmax of the compressor (20). Here, the maximum rotational speed Nmax is a predetermined value of 100 [rps] or higher, preferably a predetermined value of 120 [rps] or higher, and more preferably a predetermined value of 150 [rps] or higher.

[0087] As shown in Figure 6, the primary space (S1) is the space between the compression mechanism (40) and the electric motor (25). More precisely, the primary space (S1) is the space between the upper end surface of the first closure portion (41a) of the front head (41) and the lower ends of the stator (26) and rotor (27) of the electric motor (25). The upper end surface of the first closure portion (40a) is a flat surface located above the recess where the first reed valve is positioned. The volume V1 of the primary space (S1) corresponds to the volume of this space. However, as shown by the dashed frame of L1 in Figure 6, the volume V1 of the primary space (S1) is calculated ignoring the presence of the upper bearing portion (41b) and the rotating shaft (30). When the volume V1 is large, the refrigerant and oil separate more easily in the primary space (S1), so the oil rise rate α becomes smaller.

[0088] H1 is the height of the primary space (S1). More precisely, as shown in Figure 6, H1 is the maximum height between the upper end surface of the first closing portion (41a) of the front head (41) and the lower ends of the stator (26) and rotor (27). When the height H1 of the primary space (S1) is large, the refrigerant and oil separate more easily in the primary space (S1), so the oil rise rate α decreases.

[0089] As shown in Figure 6, the secondary space (S2) is the space above the electric motor (25). More precisely, the secondary space (S2) is the space between the upper ends of the stator (26) and rotor (27) of the electric motor (25) and the top of the casing (21) (upper cover portion (21b)). The volume V2 of the secondary space (S2) corresponds to the volume of this space. However, as shown by the dashed frame of L2 in Figure 6, the volume V2 of the secondary space (S2) is calculated ignoring the presence of the rotating shaft (30) and the discharge pipe (24). When the volume V2 is large, the refrigerant and oil separate more easily in the secondary space (S2), so the oil rise rate α becomes smaller.

[0090] H2 is the height of the secondary space (S2). More precisely, as shown in Figure 6, H2 is the maximum height between the upper ends of the stator (26) and rotor (27) of the electric motor (25) and the top (upper cover (21b)). When the height H2 of the secondary space (S2) is large, the refrigerant and oil separate more easily in the secondary space (S2), so the oil rise rate α decreases.

[0091] As shown in Figure 2, height Hc is the total height of the casing (21). In other words, height Hc is the maximum height from the bottom end to the top end of the casing (21).

[0092] When the density Dg of the refrigerant increases, the amount of refrigerant circulating in the refrigerant circuit (10) increases, making it easier for the refrigerant oil to leak out of the casing (21) along with the refrigerant. Therefore, when the density Dg of the refrigerant decreases, the oil leakage rate α decreases.

[0093] In this embodiment, the density Dg of the refrigerant is 37 [g / cm³]. 3 ] or more, 44[g / cm 3 The following applies: The density Dg of the refrigerant is smaller compared to, for example, the density of an HFC refrigerant. By reducing the density Dg of the refrigerant in this way, the oil leakage rate α can be reduced.

[0094] The density Do of the refrigerant oil is the density of the refrigerant oil. When the density of the refrigerant oil increases, it becomes more difficult for the refrigerant oil to leak out of the casing (21), and the oil leakage rate α decreases.

[0095] The dissolved viscosity η of the refrigerant oil is the dissolved viscosity of the refrigerant oil (hereinafter also referred to as the first refrigerant oil) present at a height position h1 or below the suction port (71a) of the oil reservoir (35) of the oil supply pump (71). The height position h1 of the suction port (71a) refers to the absolute height of the horizontal plane passing through the suction port (71a), as shown in Figure 3. "Dissolved viscosity" refers to the viscosity of the fluid in which the refrigerant is dissolved in the refrigerant oil. The viscosity of this fluid is measured by a method conforming to JIS K2283. The dissolved viscosity of the refrigerant oil changes depending on the content of the extreme pressure additives, antioxidants, or oxygen scavengers mentioned above.

[0096] When the dissolution viscosity η decreases, the viscous resistance of the refrigeration oil decreases, making it easier for the refrigeration oil to leak out of the casing (21). Therefore, increasing the dissolution viscosity η reduces the oil leakage rate α.

[0097] The dissolution viscosity η is preferably 5.0 or higher. This is because if the dissolution viscosity η is less than 5.0, the amount of wear at the sliding parts of the bearings (44, 45) and the sliding parts of the eccentric parts (32A, 32B) increases sharply. In addition, by increasing the dissolution viscosity η in this way, the oil consumption rate α can be reduced.

[0098] The dissolution viscosity η is preferably 1.2 or less. If the dissolution viscosity η becomes too high, the sliding loss in the eccentric parts (32A, 32B) increases, and the efficiency of the compressor (20) decreases. If the dissolution viscosity is 1.2 or less, the decrease in the efficiency of the compressor (20) can be suppressed.

[0099] As described above, each of the parameters mentioned above affects the oil consumption rate α. The inventors of this application have confirmed through verification that the oil consumption rate α can be expressed by equation (2). Therefore, by satisfying equations (1) and (2) (α=1.0), the oil consumption rate α can be kept below 1.0 even when the rotational speed N of the compressor (20) is operated at 100 [rps] or higher.

[0100] In this embodiment, as shown in equation (3), H2 / Hc ≤ 0.25. If the height of the secondary space (S2) becomes excessively large relative to the total length of the casing (21), the volume of the secondary space (S2) increases. As mentioned above, hydrocarbon refrigerants are easily soluble in refrigeration oil, so the amount of refrigerant held in the secondary space (S2) tends to increase particularly as the volume of the secondary space (S2) increases. In contrast, by setting H2 / Hc ≤ 0.25, the volume of the secondary space (S2) decreases. As a result, the amount of refrigerant held in the secondary space (S2) can be reduced. Therefore, even if the amount of refrigerant circuit (10) is limited, the amount of refrigerant used in the refrigeration cycle can be secured. In other words, a normal refrigeration cycle can be performed, and the amount of refrigerant circuit (10) can be reduced.

[0101] In this embodiment, as shown in equation (4), 0.2 ≤ H2 / Hc. If the height H2 of the secondary space (S2) is too low, the oil separation rate in the secondary space (S2) decreases, and the oil rise rate α increases. In contrast, by setting 0.2 ≤ H2 / Hc, the function of separating the refrigerant oil in the secondary space (S2) can be ensured, and the oil rise rate α can be reduced.

[0102] (6) Effects of the Embodiment (6-1) The refrigerant in this embodiment is a hydrocarbon refrigerant. The rotary compressor has N≧100[rps] and ((8.19 × 10 -8 ×Vc×Dg+0.000327)×Vc 3.657 ×N 3.126 ) / (V1×V2×H1 1.867 ×H2 1.556 The relationship ×Do×η)≦α, (α=1.0) is satisfied.

[0103] This configuration allows the oil separation rate α to be kept below 1.0 when the compressor (20) is operated at a rotational speed N of 100 [rps] or higher. As a result, shortages of refrigerant oil supplied to the bearings (44, 45) and eccentric parts (32A, 32B) can be suppressed, improving the reliability of the compressor (20).

[0104] (6-2) The compressor (20) in this embodiment satisfies the relationship H2 / Hc ≤ 0.25. This reduces the amount of refrigerant held in the secondary space (S2). Therefore, it is possible to limit the amount of refrigerant charged into the refrigerant circuit (10) while suppressing a shortage of refrigerant used in the refrigeration cycle.

[0105] (6-3) The compressor (20) of this embodiment satisfies the relationship 0.2 ≤ H2 / Hc. This ensures the function of oil separation in the secondary space (S2), thereby reducing the oil consumption rate.

[0106] (6-4) Refrigeration oil contains either polyalkylene glycol, polyvinyl ether, or polyol ester.

[0107] By using these refrigeration oils, hydrocarbon refrigerants are less likely to dissolve into the refrigeration oil. Therefore, the decrease in the viscous resistance of the refrigeration oil can be suppressed, thus reducing the rate of oil consumption. In addition, since the dissolution viscosity of the first refrigeration oil does not become excessively low, wear on sliding parts can be suppressed. In particular, by setting the molecular weight of the refrigeration oil between 1000 and 1800, the dissolution of hydrocarbon refrigerants into the refrigeration oil can be effectively suppressed.

[0108] In addition, by suppressing the dissolution of hydrocarbon refrigerant into the refrigeration oil in this manner, the amount of refrigerant held within the casing (21) is reduced. Therefore, it is possible to limit the amount of refrigerant charged into the refrigeration circuit (10) while preventing a shortage of refrigerant used in the refrigeration cycle.

[0109] (6-5) The refrigeration oil contains at least one of the following: an extreme pressure additive of phosphate esters, an antioxidant, and an acid scavenger.

[0110] When refrigerant oil contains antioxidants, it contains 0.1% by weight or more and 0.5% by weight or less of antioxidants. Hydrocarbon refrigerants have a chemically stable structure and are less prone to decomposition during the refrigeration cycle compared to HFC and HFO refrigerants. Therefore, even if the amount of antioxidant is 0.5% by weight or less, the refrigerant can be used stably over the long term. Furthermore, by limiting the amount of antioxidant to 0.5% by weight or less, the decrease in viscosity of the refrigerant oil can be suppressed. As a result, the viscous resistance of the refrigerant oil increases, which reduces the oil consumption rate α. In addition, wear on sliding parts can be suppressed.

[0111] When refrigerant oil contains an acid scavenger, it contains 0.1% to 0.5% by weight of the acid scavenger. As mentioned above, hydrocarbon refrigerants have a chemically stable structure and are less prone to decomposition during the refrigeration cycle compared to HFC and HFO refrigerants. Therefore, even if the amount of acid scavenger is 0.5% by weight or less, the refrigerant can be used stably over the long term. Furthermore, by limiting the amount of antioxidant to 0.5% by weight or less, the decrease in viscosity of the refrigerant oil can be suppressed. As a result, the viscous resistance of the refrigerant oil increases, which reduces the oil consumption rate α. In addition, wear on sliding parts can be suppressed.

[0112] When refrigeration oil contains extreme pressure additives, it contains 1.0% to 5.0% by weight of extreme pressure additives. By limiting the amount of extreme pressure additives to 5.0% by weight or less, the decrease in viscosity of the refrigeration oil can be suppressed. As a result, the viscous resistance of the refrigeration oil increases, which reduces the oil consumption rate α. In addition, wear on sliding parts can be suppressed.

[0113] (7) Other embodiments A rotary compressor may be of the so-called rolling piston type, in which vanes separate from the rollers are in contact with the rollers while the rollers rotate eccentrically. Alternatively, a rotary compressor may be of the so-called hinge vane type, in which the tips of the vanes are rotatably fitted into recesses on the outer surface of the rollers while the rollers rotate eccentrically.

[0114] The compression mechanism (40) may have only one cylinder or may have three or more cylinders. In other words, the compression mechanism (40) may have only one compression section or may have three or more compression sections.

[0115] The air conditioning system (1) may be an indoor multi-type system having multiple indoor units. The air conditioning system (1) may be a movable type that adjusts the temperature of the air in a target space such as a vehicle. The refrigeration cycle system may be a hot water supply system for generating hot water, or a cooling system for generating chilled water. The refrigeration cycle system may be an in-cabin cooling system for cooling the air inside the compartment. The in-cabin cooling system may be a stationary type for warehouses, or a movable type for the interior of transport containers or trailers.

[0116] The rotary compressor (20) may satisfy only equations (1) and (2) above, but it is preferable that it also satisfies equation (3) or (4).

[0117] The first refrigerant oil is the refrigerant oil in the oil reservoir (35) that is below the height of the suction port (71a). However, it is preferable that the first refrigerant oil is the refrigerant oil that is located below the suction port (71a), near the suction port (71a), or inside the suction port (71a).

[0118] While embodiments and modifications have been described above, it will be understood that a variety of changes in form and details are possible without departing from the spirit and scope of the claims. Furthermore, the embodiments, modifications, and other embodiments described above may be combined or substituted as appropriate, as long as they do not impair the functions covered by this disclosure.

[0119] The designations "1st," "2nd," "3rd," etc., mentioned above are used to distinguish between the terms to which these designations are attached, and do not limit the number or order of those terms. [Industrial applicability]

[0120] As described above, this disclosure is useful for rotary compressors and refrigeration cycle systems. [Explanation of Symbols]

[0121] 1. Air conditioning system (refrigeration cycle system) 10 Refrigerant Circuit 20 Compressors 21 Casing 24 Discharge pipe 25 Electric motor 30 Rotation axis 40 Compression mechanism 51A, 51B Cylinder 52A, 52B Roller 53A, 53B vanes 70 Fueling mechanism 71a Inlet S interior space S1 primary space S2 Secondary space

Claims

1. Electric motor (25), A rotating shaft (30) connected to the electric motor (25), A compression mechanism (40) is positioned below the electric motor (25) and is driven by the rotating shaft (30) to compress the refrigerant, A casing (21) that houses the electric motor (25), the rotating shaft (30), and the compression mechanism (40), and whose interior is filled with high-pressure refrigerant discharged from the compression mechanism (40), The casing (21) has a suction port (71a) for sucking up the refrigerant oil accumulated at its bottom, and is equipped with a lubrication mechanism (70) for supplying the refrigerant oil to the sliding parts. The compression mechanism (40) includes an annular cylinder (51A, 51B), an annular roller (52A, 52B) that rotates eccentrically within the cylinder (51A, 51B), and vanes (53A, 53B) for forming a compression chamber within the cylinder (51A, 51B). The internal space (S) of the casing (21) includes a primary space (S1) between the compression mechanism (40) and the electric motor (25), and a secondary space (S2) above the electric motor (25). A discharge pipe (24) is connected to the casing (21) and communicates with the secondary space (S2). The refrigerant is a single refrigerant consisting of a hydrocarbon refrigerant, or a mixed refrigerant containing said hydrocarbon refrigerant. The displacement volume of the compression mechanism (40) is Vc [cc], The density of the aforementioned refrigerant at 1.9 MPa and 75°C is Dg [g / cm³]. 3 ], Let the rotational speed of the aforementioned rotating shaft (30) be N [rps]. Let V1 [cc] be the volume of the primary space (S1) Let the volume of the secondary space (S2) be V2 [cc]. Let the height of the primary space (S1) be H1 [cm]. Let the height of the secondary space (S2) be H2 [cm]. The density of the aforementioned refrigerant oil at 15°C is Do[g / cm³] 3 ], If we define the dissolution viscosity of the refrigerant oil present at or below the height of the aforementioned suction port (71a) as η [mPa・S], N ≥ 100 [rps] and, ((8.19 x 10 -8 ×Vc × Dg + 0.000327) × Vc 3.657 ×N 3.126 ) / (V1×V2×H1 1.867 ×H2 1.556 The relationship ×Do ​​× η) ≤ 1.0 is satisfied. Rotary compressor.

2. If we define the total height of the casing (21) as Hc [cm], H2 / Hc ≤ 0.25 The rotary compressor according to claim 1.

3. If we define the total height of the casing (21) as Hc [cm], 0.2 ≤ H2 / HC The rotary compressor according to claim 1.

4. The refrigeration oil contains one of the following: polyalkylene glycol, polyvinyl ether, or polyol ester. A rotary compressor according to any one of claims 1 to 3.

5. The density Do [g / cm 3 of the refrigerant is 37 [g / cm 3 or more and 44 [g / cm 3 or less A rotary compressor according to any one of claims 1 to 3.

6. The refrigeration oil contains at least one of the following: an extreme pressure additive of phosphate esters, an antioxidant, and an acid scavenger. A rotary compressor according to any one of claims 1 to 3.

7. The aforementioned refrigeration oil contains 0.1% or more and 0.5% or less by weight of an antioxidant or acid scavenger. The rotary compressor according to claim 6.

8. The refrigeration oil contains 1.0% by weight or more and 5.0% by weight or less of extreme pressure additives. The rotary compressor according to claim 6.

9. The molecular weight of the refrigeration oil is 1000 or more and 1800 or less. A rotary compressor according to any one of claims 1 to 3.

10. The rotary compressor (20) according to any one of claims 1 to 3, and the refrigerant circuit (10) that performs a refrigeration cycle using a hydrocarbon refrigerant, are provided. Refrigeration cycle device.

Images