Scroll compressor and refrigeration cycle device

Abstract

In a scroll compressor 100, oil introduction holes 51, 61 for introducing oil into a discharge oil passage 64 in an intermediate pressure region (M) are formed in a fixed scroll key groove 11k of a fixed scroll 11, whereby oil passes through an Oldham ring key 17k and the fixed scroll key groove 11k or a turning scroll key groove 12k, and sufficient oil can be supplied to sliding surfaces of the Oldham ring key 17k and the key groove 11k, 12k. Accordingly, a scroll compressor with high efficiency and high reliability can be provided.

Description

Scroll compressor and refrigeration cycle device

[0001] The present disclosure relates to a scroll compressor used in a refrigeration machine, particularly an air conditioner, a water heater, or a refrigerator, and a refrigeration cycle device using the scroll compressor.

[0002] Patent Document 1 discloses a scroll compressor used in air conditioners and the like. This scroll compressor has a recess formed on the surface of the Oldham ring key that faces the bottom surface of the keyway of the orbiting scroll or the fixed scroll, or on the surface of the orbiting scroll that faces the top surface of the Oldham ring key. The movement of the Oldham ring causes oil to be drawn up, and some of the oil accumulates in the recess. This prevents poor oil supply between the Oldham ring key and the keyway of the fixed scroll or the orbiting scroll, improving compressor reliability. However, this configuration has issues, such as the oil being unable to reach the recess, which is high above the oil surface, during low-speed operation when the oil supply amount is extremely low, and the oil being unable to accumulate in the recess when the compressor is horizontal.

[0003] JP 2019-100254 A

[0004] The present disclosure can provide a more efficient and reliable scroll compressor that can directly supply oil to the sliding surfaces of the Oldham ring key and the fixed scroll keyway or the Oldham ring key and the orbiting scroll keyway, and that can also be used with horizontal compressors.

[0005] The scroll compressor of the present disclosure is configured such that the orbiting scroll and the fixed scroll are pressed against each other by an intermediate pressure region formed on the opposite wrap surface side of the orbiting scroll end plate or the opposite wrap surface side of the fixed scroll end plate, and the oil discharge path from the intermediate pressure region to the compression chamber is configured to pass through one or more of the fixed scroll key grooves or the orbiting scroll key grooves.

[0006] According to the scroll compressor of the present disclosure, the oil supplied to the intermediate pressure region passes reliably through the fixed scroll keyway on its way to the compression chamber, thereby allowing sufficient oil to be supplied to the sliding surface with the Oldham ring key, resulting in a scroll compressor with higher efficiency and reliability.

[0007] FIG. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment; FIG. 2 is an enlarged sectional view of a main part showing a compression mechanism of the scroll compressor; FIG. 3 is an enlarged view of a main part showing a compression mechanism of the scroll compressor; FIG. 4 is a view for explaining an outlet of an oil path for supplying oil to an intermediate pressure region according to the first embodiment; and FIG. 5 is a sectional view for explaining a substantially closed space (C) according to the first embodiment.

[0008] (Findings, etc., that formed the basis of the present disclosure) At the time the inventors arrived at the present disclosure, scroll compressors typically supplied oil to the sliding surfaces between the Oldham ring key and the fixed scroll keyway, or between the Oldham ring key and the orbiting scroll keyway, by splashing oil collected in the intermediate pressure region where the Oldham ring is located due to the movement of the components (the Oldham ring and the orbiting scroll), with some of the oil adhering to the sliding surfaces, thereby ensuring lubrication. However, with this configuration, for example, when the compressor continued to operate at low speeds, the force that splashes the oil weakened due to the movement of the components, making it impossible to maintain the lubrication of the sliding surfaces. This could lead to increased frictional resistance, a deterioration in input power, and reduced reliability. The inventors came up with the subject matter of the present disclosure in order to solve this problem.

[0009] The present disclosure provides a scroll compressor that is more efficient and reliable by allowing oil to be directly supplied to the sliding surfaces between the Oldham ring key and the fixed scroll keyway, or between the Oldham ring key and the orbiting scroll keyway.

[0010] Hereinafter, embodiments will be described in detail with reference to the drawings. However, more detailed description than necessary may be omitted. For example, detailed description of already well-known matters or redundant description of substantially identical configurations may be omitted. This is to avoid unnecessary redundancy in the following description and to facilitate understanding by those skilled in the art. Note that the accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the present disclosure, and are not intended to limit the subject matter described in the claims.

[0011] First Embodiment Hereinafter, a first embodiment will be described with reference to FIGS.

[0012] [1-1. Configuration] As shown in FIG. 1 , a scroll compressor 100 includes a compression mechanism 10 that compresses a refrigerant and an electric mechanism 20 that drives the compression mechanism 10, both of which are arranged within a sealed container 1. The sealed container 1 includes a cylindrical body 1a extending vertically, a lower lid 1b that closes a lower opening of the body 1a, and an upper lid 1c that closes an upper opening of the body 1a. The sealed container 1 is provided with a refrigerant suction pipe 2 that introduces refrigerant into the compression mechanism 10 and a refrigerant discharge pipe 3 that discharges the refrigerant compressed by the compression mechanism 10 to the outside of the sealed container 1. The compression mechanism 10 includes a fixed scroll 11, an orbiting scroll 12, and a rotating shaft 13 that orbits the orbiting scroll 12. The electric mechanism 20 includes a stator 21 fixed to the sealed container 1 and a rotor 22 arranged inside the stator 21. The rotating shaft 13 is fixed to the rotor 22. An eccentric shaft 13a is formed at the upper end of the rotary shaft 13, and is eccentric with respect to the rotary shaft 13. The distance between the center line of the rotary shaft 13 and the center line of the eccentric shaft 13a is the turning radius.

[0013] The main bearing 30 is provided below the fixed scroll 11 and the orbiting scroll 12. The main bearing 30 supports the fixed scroll 11 and the orbiting scroll 12. The main bearing 30 is formed with a bearing portion 31 that supports the rotating shaft 13, and a boss accommodating portion 32. The main bearing 30 is fixed to the sealed container 1 by welding, shrink fitting, or the like.

[0014] The fixed scroll 11 includes a disk-shaped fixed scroll end plate 11a, a spiral-shaped fixed spiral wrap 11b extending from the fixed scroll end plate 11a, and an outer peripheral wall portion 11c extending to surround the fixed spiral wrap 11b. A discharge port 14 is formed approximately at the center of the fixed scroll end plate 11a. The orbiting scroll 12 includes a disk-shaped orbiting scroll end plate 12a, an orbiting spiral wrap 12b extending from one surface (the wrap-side end surface) of the orbiting scroll end plate 12a, and a cylindrical boss portion 12c formed on the other surface (the anti-wrap-side end surface) of the orbiting scroll end plate 12a. The other surface of the orbiting scroll end plate 12a is the surface opposite the wrap-side end surface of the orbiting scroll end plate 12a.

[0015] As shown in FIG. 2( a), the orbiting bearing 13d is fitted into the cylindrical boss portion 12c. The wrap side of the orbiting bearing 13d is closed by the orbiting scroll end plate 12a, and the opposite wrap side is open. The eccentric shaft 13a of the rotating shaft 13 is inserted into the boss portion 12c from the open side of the orbiting bearing 13d. The fixed spiral wrap 11b of the fixed scroll 11 and the orbiting spiral wrap 12b of the orbiting scroll 12 are intermeshed with each other, forming multiple compression chambers 15 between the fixed spiral wrap 11b and the orbiting spiral wrap 12b. The boss portion 12c is formed approximately in the center of the orbiting scroll end plate 12a. The boss portion 12c is accommodated in the boss accommodating portion 32 with the eccentric shaft 13a inserted into the boss portion 12c. The fixed scroll 11 is fixed to the main bearing 30 at its outer peripheral wall portion 11c using multiple bolts (not shown). On the other hand, the movement of the orbiting scroll 12 relative to the fixed scroll 11 is restricted by the Oldham ring 17 .

[0016] As shown in FIG. 2(c), the Oldham ring 17 has Oldham ring keys 17k arranged on the ring circumference so that they face each other at right angles. Each Oldham ring key 17k slidably contacts the orbiting scroll key groove 12k and the fixed scroll key groove 11k, respectively. As shown in FIG. 3(c), the orbiting scroll key groove 12k is formed on the other surface (the end surface opposite the wrap) of the orbiting scroll end plate 12a. As shown in FIG. 2(b), the fixed scroll key groove 11k is formed on the outer peripheral wall portion 11c of the fixed scroll 11. While the fixed scroll key groove 11k is formed on the fixed scroll 11 in this embodiment, it may also be formed on the main bearing 30.

[0017] As shown in FIG. 3( c), the orbiting scroll keyway 12k is composed of a pair of orbiting scroll keyway first side surfaces 12k1, an orbiting scroll keyway second side surface 12k2, and an orbiting scroll keyway bottom surface 12k3. The pair of orbiting scroll keyway first side surfaces 12k1 and the orbiting scroll keyway bottom surface 12k3 are formed by surfaces parallel to the direction (Y) in which the Oldham ring 17 moves relative to the orbiting scroll 12. The pair of orbiting scroll keyway first side surfaces 12k1 are formed by opposing parallel surfaces. The orbiting scroll keyway bottom surface 12k3 is formed by a surface perpendicular to the orbiting scroll keyway first side surfaces 12k1 and is formed between the pair of orbiting scroll keyway first side surfaces 12k1. The orbiting scroll keyway second side surface 12k2 is formed by a surface perpendicular to the pair of orbiting scroll keyway first side surfaces 12k1 and the orbiting scroll keyway bottom surface 12k3. The pair of orbiting scroll keyway first side surfaces 12k1 come into contact with and slide on the Oldham ring key 17k, while the orbiting scroll keyway second side surface 12k2 and the orbiting scroll keyway bottom surface 12k3 do not come into contact with and slide on the Oldham ring key 17k.

[0018] As shown in FIG. 3A, the fixed scroll keyway 11k is composed of a pair of fixed scroll keyway first side surfaces 11k1, a pair of fixed scroll keyway second side surfaces 11k2, and a fixed scroll keyway bottom surface 11k3. The pair of fixed scroll keyway first side surfaces 11k1 and the fixed scroll keyway bottom surface 11k3 are formed by surfaces parallel to the direction (X) in which the Oldham ring 17 moves relative to the fixed scroll 11. The pair of fixed scroll keyway first side surfaces 11k1 are formed by opposing parallel surfaces. The pair of fixed scroll keyway second side surfaces 11k2 are formed by opposing parallel surfaces. The fixed scroll keyway bottom surface 11k3 is formed by a surface perpendicular to the fixed scroll keyway first side surfaces 11k1 and is formed between the pair of fixed scroll keyway first side surfaces 11k1. The fixed scroll keyway bottom surface 11k3 is formed by a surface perpendicular to the fixed scroll keyway second side surfaces 11k2 and is formed between the pair of fixed scroll keyway second side surfaces 11k2. The first side surfaces 11k1 of the pair of fixed scroll keyways contact and slide against the Oldham ring key 17k. The second side surfaces 11k2 of the pair of fixed scroll keyways and the bottom surface 11k3 of the fixed scroll keyway do not contact and slide against the Oldham ring key 17k. As a result, the orbiting scroll 12 orbits relative to the fixed scroll 11 without rotating as the eccentric shaft 13a of the rotating shaft 13 rotates.

[0019] As shown in FIG. 1 , an oil reservoir 4 for storing lubricating oil is formed at the bottom of the sealed container 1. The lower end 13b of the rotating shaft 13 is journaled on a sub-bearing 18 located at the bottom of the sealed container 1. A positive displacement oil pump 5 is provided at the lower end of the rotating shaft 13. The oil pump 5 is positioned so that its suction port is located within the oil reservoir 4. The oil pump 5 is driven by the rotating shaft 13 and reliably draws up lubricating oil from the oil reservoir 4 located at the bottom of the sealed container 1 regardless of pressure conditions, eliminating concerns about running out of oil supply. The rotating shaft 13 is formed with a rotating shaft oil supply hole 13c extending from the lower end 13b of the rotating shaft 13 to the eccentric shaft 13a. The oil drawn up by the oil pump 5 is supplied through the rotating shaft oil supply hole 13c formed in the rotating shaft 13 to the bearing of the sub-bearing 18, the bearing portion 31, and the boss portion 12c. As shown in Figure 2(a), oil that reaches a high-pressure region (H) surrounded by the boss portion 12c, the anti-wrap side surface of the orbiting scroll end plate 12a, and the upper end surface of the eccentric shaft 13a is supplied to the orbiting bearing 13d and the boss accommodating portion 32 by an oil groove 13e formed in the outer circumferential surface of the eccentric shaft 13a. The oil groove 13e may be a spiral groove or a D-cut. A seal member 33 is provided on the outer periphery of the boss accommodating portion 32, so the interior of the boss accommodating portion 32 becomes high-pressure.

[0020] Refrigerant sucked through the refrigerant suction pipe 2 is guided through the suction port 15a into the compression chamber 15. The compression chamber 15 moves from the outer periphery toward the center while its volume decreases. When the refrigerant reaches a predetermined pressure in the compression chamber 15, it is discharged into the discharge chamber 6 through the discharge port 14 provided in the center of the fixed scroll 11. A discharge reed valve (not shown) is provided in the discharge port 14. When the refrigerant reaches a predetermined pressure in the compression chamber 15, it pushes open the discharge reed valve, and the refrigerant is discharged into the discharge chamber 6. The refrigerant discharged into the discharge chamber 6 is led into the sealed container 1 and discharged from the refrigerant discharge pipe 3.

[0021] In the refrigeration cycle apparatus according to this embodiment, a scroll compressor 100, a condenser 111, a pressure reducing device 112, and an evaporator 113 are connected in a ring shape by piping. The condenser 111 condenses the refrigerant discharged from the refrigerant discharge pipe 3, the pressure reducing device 112 reduces the pressure of the refrigerant condensed in the condenser 111, and the evaporator 113 evaporates the refrigerant reduced in pressure by the pressure reducing device 112. The refrigerant evaporated in the evaporator 113 is returned to the scroll compressor 100.

[0022] 2(a), the scroll compressor 100 of this embodiment has a high-pressure region (H) surrounded by the boss portion 12c, the orbiting scroll end plate 12a, and the upper end of the eccentric shaft 13a, and an intermediate-pressure region (M) outside the seal member 33. The Oldham ring 17 is disposed in the intermediate-pressure region (M).

[0023] The configuration is described below. As shown in FIG. 2( a), the eccentric shaft 13a is inserted into the boss portion 12c via an orbiting bearing 13d so as to be orbitally drivable. A ring-shaped groove is formed in the surface of the main bearing 30 facing the non-wrap surface of the orbiting scroll end plate 12a. A ring-shaped seal member 33 is disposed in this ring-shaped groove. The seal member 33 is disposed on the outer periphery of the boss accommodating portion 32. The boss accommodating portion 32, which is a high-pressure region (H), is separated from the intermediate-pressure region (M) by the seal member 33. The sealed container 1 is filled with a high-pressure refrigerant at the same pressure as the refrigerant discharged into the discharge chamber 6. The rotating shaft oil supply hole 13c opens at the upper end of the eccentric shaft 13a. Therefore, the oil that reaches the high-pressure region (H) surrounded by the boss portion 12c, the orbiting scroll end plate 12a, and the upper end of the eccentric shaft 13a is under pressure conditions equivalent to the pressure of the discharged refrigerant. A portion of the oil that reaches the high-pressure region (H) is intermittently supplied to the intermediate-pressure region (M) through an oil supply passage 54 provided in the orbiting scroll end plate 12a, and is supplied to the sliding surfaces of the Oldham ring key 17k and the fixed scroll key groove 11k, the Oldham ring key 17k and the orbiting scroll key groove 12k, etc.

[0024] 2(a) and 3(c), the oil supply path 54 is composed of a first oil inlet hole 51 formed in the rotational axis direction toward the inside of the boss portion 12c, a first oil outlet hole 52 opening at the outer periphery of the wrap-side end face, and a first oil communication passage 53 connecting the first oil inlet hole 51 and the first oil outlet hole 52. As shown in FIGS. 2(a) and 2(b), the fixed scroll 11 is formed with an oil drain path 64 through which oil flows from the intermediate pressure region (M) to the compression chamber 15 whose pressure is lower than that of the intermediate pressure region (M). The oil drain path 64 is composed of a second oil inlet hole 61 opening at the intermediate pressure region (M), a second oil outlet hole 62 opening at the compression chamber 15 whose pressure is lower than that of the intermediate pressure region (M), and a second oil communication passage 63 connecting the second oil inlet hole 61 and the second oil outlet hole 62. As shown in Figures 2(b), 3(a), and 3(b), an oil communication groove 11o is formed in the fixed scroll 11. The oil communication groove 11o transfers oil supplied from the first oil discharge hole 52 formed in the orbiting scroll 12 to the intermediate pressure region (M). As shown in Figure 3(b), the first oil discharge hole 52 and the oil communication groove 11o intermittently communicate with each other as the rotating shaft 13 rotates.

[0025] In this configuration, the intermediate pressure region (M), located relatively farther outward on the anti-wrap side of the orbiting scroll end plate 12a, has a lower pressure than the high pressure region (H), reducing the pressure difference with the internal pressure of the compression chamber 15. This allows the orbiting scroll 12 to be pressed against the fixed scroll 11 with the minimum necessary load under various operating conditions. This reduces friction loss in the scroll compressor 100, prevents the orbiting scroll 12 from separating from the fixed scroll 11, and improves the airtightness of the compression chamber 15.

[0026] Although the present embodiment describes a configuration in which the orbiting scroll 12 is pressed against the fixed scroll 11, a configuration in which the intermediate-pressure region (M) is located on the side opposite the wrap surface of the fixed scroll end plate and the fixed scroll 11 is pressed against the orbiting scroll 12 may also be used. Here, the second oil inlet hole 61 opening into the intermediate-pressure region (M) is formed in one of the surfaces constituting the fixed scroll keyway 11k (the first side surface 11k1 of the fixed scroll keyway, the second side surface 11k2 of the fixed scroll keyway, or the bottom surface 11k3 of the fixed scroll keyway). By forming the second oil inlet hole 61 in the fixed scroll keyway 11k, oil in the intermediate-pressure region (M) is guided via the fixed scroll keyway 11k to the compression chamber 15, which has a lower pressure than the intermediate-pressure region (M). Therefore, oil is reliably supplied to the fixed scroll keyway 11k. By forming the second oil inlet hole 61 in one of the surfaces constituting the fixed scroll keyway 11k, oil can be reliably supplied to the fixed scroll keyway 11k (Configuration A). In the scroll compressor 100 of this embodiment, the second oil introduction hole 61 is formed in the bottom surface 11k3 of the fixed scroll keyway. The pair of fixed scroll keyway second side surfaces 11k2 and the fixed scroll keyway bottom surface 11k3 do not come into contact with and slide on the Oldham ring key 17k. Therefore, it is preferable to provide the second oil introduction hole 61 in the pair of fixed scroll keyway second side surfaces 11k2 and the fixed scroll keyway bottom surface 11k3.

[0027] The oil communication groove 11o also communicates with the fixed scroll keyway 11k (outlet (D) shown in FIG. 3(a)). Because oil is intermittently supplied to the oil communication groove 11o from the second oil outlet hole 62, the oil intermittently supplied to the oil communication groove 11o is supplied to the fixed scroll keyway 11k. The oil supplied to the fixed scroll keyway 11k is led to the intermediate pressure region (M) by the pressure difference.

[0028] The oil outlet (D) of the oil communication groove 11o is formed to open only to one of the surfaces (the first side surface 11k1 of the fixed scroll keyway, the second side surface 11k2 of the fixed scroll keyway, or the bottom surface 11k3 of the fixed scroll keyway) that make up the fixed scroll keyway 11k. This ensures that the oil passes through the fixed scroll keyway 11k as it moves from the oil communication groove 11o to the intermediate-pressure region (M) (Configuration B). A configuration combining the above-described (Configuration A) and (Configuration B) is also preferable. That is, oil in the high-pressure region (H) is guided to the intermediate-pressure region (M) via the oil supply path 54 provided in the orbiting scroll end plate 12a via one of the fixed scroll keyways 11k, and oil in the intermediate-pressure region (M) is guided to the compression chamber 15, whose pressure is lower than that of the intermediate-pressure region (M), via the other fixed scroll keyway 11k via the oil drain path 64. This ensures that oil is supplied to the pair of fixed scroll keyways 11k.

[0029] In the scroll compressor 100 of this embodiment, the opening position (outlet) (D) of the oil communication groove 11o to the intermediate pressure region (M) is formed on the second side surface 11k2 of the fixed scroll keyway of the fixed scroll 11, as shown in Fig. 5. The pair of fixed scroll keyway second side surfaces 11k2 and the fixed scroll keyway bottom surface 11k3 do not come into contact with and slide on the Oldham ring key 17k. Therefore, it is preferable to provide the opening position (outlet) (D) of the oil communication groove 11o on the pair of fixed scroll keyway second side surfaces 11k2 and the fixed scroll keyway bottom surface 11k3.

[0030] FIG. 4 illustrates a scroll compressor 100 in which the fixed scroll 11 does not have a keyway, but the orbiting scroll 12 and the main bearing 30 have keyways. In the scroll compressor 100 shown in FIG. 4 , the second oil inlet hole 61 is formed to open to the thrust surface of the fixed scroll 11 relative to the orbiting scroll end plate 12a. The orbiting scroll keyway bottom surface 12k3 is formed with a sub-second oil inlet hole 61s penetrating the orbiting scroll end plate 12a. The orbiting motion of the orbiting scroll 12 intermittently connects the second oil inlet hole 61 and the sub-second oil inlet hole 61s. This configuration ensures that oil passes through the orbiting scroll keyway 12k reliably during its movement from the intermediate pressure region (M) to the compression chamber 15 (Configuration AA). The orbiting scroll keyway bottom surface 12k3 is formed with a sub-first oil inlet hole 51s penetrating the orbiting scroll end plate 12a. The oil communication groove 11o arranged in the fixed scroll 11 and the first sub-oil introduction hole 51s are configured to intermittently communicate with each other. With this configuration, the oil reliably passes through the orbiting scroll key groove 12k as it moves from the oil communication groove 11o to the intermediate pressure region (M) (Configuration BB). A configuration that combines the above-described (Configuration AA) and (Configuration BB) is also preferable.

[0031] [1-2. Operation] In the scroll compressor 100 configured as described above, by providing the second oil introduction hole 61 in the fixed scroll keyway bottom surface 11k3 or by providing the sub-second oil introduction hole 61s in the orbiting scroll keyway bottom surface 12k3, oil reliably passes through the fixed scroll keyway 11k or the orbiting scroll keyway 12k in the process of moving from the intermediate pressure region (M) to the compression chamber 15. Furthermore, by configuring the oil communication groove 11o arranged in the fixed scroll 11 to communicate only with the fixed scroll keyway second side surface 11k2 or the orbiting scroll keyway bottom surface 12k3, oil reliably passes through the fixed scroll keyway 11k or the orbiting scroll keyway 12k in the process of moving from the oil communication groove 11o to the intermediate pressure region (M).

[0032] [1-3. Effects, etc.] In the scroll compressor 100 of this embodiment, the second oil inlet hole 61, which is one of the oil drain passages 64 provided in the fixed scroll 11 and opens into the intermediate-pressure region (M), is formed in one of the surfaces (the first side surface 11k1 of the fixed scroll keyway, the second side surface 11k2 of the fixed scroll keyway, or the bottom surface 11k3 of the fixed scroll keyway) that constitute the fixed scroll keyway 11k in which the Oldham ring key 17k is disposed. As shown in FIG. 2 , by forming the second oil inlet hole 61 in the bottom surface 11k3 of the fixed scroll keyway, oil reliably passes through the fixed scroll keyway 11k during the process of discharging oil from the intermediate-pressure region (M) to the compression chamber 15 (Configuration A). According to this configuration, oil supplied to the intermediate-pressure region (M) reliably passes through the fixed scroll keyway 11k during the process of being delivered to the compression chamber 15. Therefore, sufficient oil can be supplied to the sliding surface with the Oldham ring key 17k, resulting in a scroll compressor 100 with higher efficiency and reliability.

[0033] Furthermore, in the scroll compressor 100 of this embodiment, the oil communication groove 11o disposed in the fixed scroll 11 is intermittently supplied with oil from the second oil outlet hole 62 provided in the orbiting scroll end plate 12a, and the oil outlet (D) from the oil communication groove 11o to the intermediate-pressure region (M) is configured to open only to one of the surfaces constituting the fixed scroll keyway 11k (the first side surface 11k1 of the fixed scroll keyway, the second side surface 11k2 of the fixed scroll keyway, or the bottom surface 11k3 of the fixed scroll keyway). This ensures that oil passes through the fixed scroll keyway 11k as it moves from the oil communication groove 11o to the intermediate-pressure region (M) (Configuration B). In this way, oil passes through the fixed scroll keyway 11k as it moves from the oil communication groove 11o to the medium-pressure chamber region (M). This ensures that sufficient oil is supplied to the sliding surface of the Oldham ring key 17k, resulting in a scroll compressor 100 with higher efficiency and reliability.

[0034] Furthermore, by combining (Configuration A) and (Configuration B), oil can be supplied to the two fixed scroll keyways 11k during the oil supply process to the intermediate pressure region (M) and the oil drain process from the intermediate pressure region (M), thereby achieving a more efficient and reliable scroll compressor 100. Furthermore, in a horizontal scroll compressor 100 in which the rotating shaft 13 is installed horizontally, oil can be supplied to the fixed scroll keyways 11k that are located at a higher position than the oil surface.

[0035] In a scroll compressor 100 in which the fixed scroll 11 does not have a keyway but the orbiting scroll 12 and the main bearing 30 have keyways, as shown in FIG. 4 , the second oil inlet hole 61 of the fixed scroll 11 is formed to open to the thrust surface of the orbiting scroll end plate 12a, and a sub-second oil inlet hole 61s is formed in the orbiting scroll keyway bottom surface 12k3, penetrating the orbiting scroll end plate 12a. The second oil inlet hole 61 and the sub-second oil inlet hole 61s are intermittently connected by the orbiting motion of the orbiting scroll 12. With this configuration, oil reliably passes through the orbiting scroll keyway 12k as it moves from the intermediate-pressure region (M) to the compression chamber 15 (Configuration AA). This allows sufficient oil to be supplied to the sliding surface of the Oldham ring key 17k, resulting in a scroll compressor 100 with higher efficiency and reliability.

[0036] 4, in a scroll compressor 100 in which the fixed scroll 11 does not have a key groove and the orbiting scroll 12 and the main bearing 30 have key grooves, the oil communication groove 11o and the first sub-oil introduction hole 51s are configured to intermittently communicate with each other, so that the oil reliably passes through the orbiting scroll key groove 12k as it moves from the oil communication groove 11o to the intermediate pressure region (M) (configuration BB). Therefore, a sufficient amount of oil can be supplied to the sliding surface with the Oldham ring key 17k, resulting in a scroll compressor 100 with higher efficiency and reliability.

[0037] Note that (Configuration AA) and (Configuration BB) can be combined with one keyway 11k and one keyway 12k, respectively, to form configurations (Configuration AB and Configuration BA). This allows oil to be selectively supplied to two keyways 11k and 12k during the oil supply process to the intermediate pressure region (M) and the oil drain process from the intermediate pressure region (M). In a horizontal scroll compressor in which the rotating shaft 13 is installed horizontally, oil can be supplied to the orbiting scroll keyway 12k and the fixed scroll keyway 11k, which are located higher than the oil level. Furthermore, to ensure that oil always passes through the keyways, it is desirable to have one oil drain path 64 connecting the intermediate pressure region (M) and the compression chamber 15, and one oil outlet (D) from the oil communication groove 11o to the intermediate pressure region (M).

[0038] As shown in FIG. 5 , the outlet (D) for oil supplied to the oil communication groove 11o to the intermediate pressure region (M) is configured to open into a substantially enclosed space (C) surrounded by the surface of the fixed scroll keyway 11k, one of the surfaces of the Oldham ring key 17k, and the orbiting scroll end plate 12a. The volume of the substantially enclosed space (C) changes with the orbiting motion of the orbiting scroll 12. Therefore, the oil and refrigerant supplied to the substantially enclosed space (C) are compressed as the volume of the substantially enclosed space (C) decreases and enter the fitting gap between the Oldham ring key 17k and the fixed scroll keyway 11k. This allows an oil film to form in the fitting gap between the Oldham ring key 17k and the fixed scroll keyway 11k, even under low-speed operating conditions where extremely little oil is supplied, thereby maintaining high reliability. The scroll compressor 100 according to this embodiment can ensure lubrication, particularly during low-speed operation at 40 rpm or less, and is therefore suitable for variable-speed operation, for example, by incorporating a frequency conversion function.

[0039] The present disclosure has been described above using the above-mentioned embodiments. However, since the above-mentioned embodiments are intended to illustrate the technology in the present disclosure, various modifications, substitutions, additions, omissions, etc. can be made within the scope of the claims or their equivalents.

[0040] The scroll compressor according to the present disclosure can achieve high efficiency and is therefore useful for various refrigeration cycle devices such as hot water heating systems, indoor air conditioners, vehicle air conditioners, water heaters, refrigerators, showcases, chillers, or freezers.

[0041] DESCRIPTION OF SYMBOLS 1 Sealed container 1a Body 1b Bottom cover 1c Top cover 2 Refrigerant suction pipe 3 Refrigerant discharge pipe 4 Oil storage section 5 Oil pump 6 Discharge chamber 10 Compression mechanism section 11 Fixed scroll 11a Fixed scroll end plate 11b Fixed spiral wrap 11c Outer circumferential wall section 11o Oil communication groove 11k Fixed scroll keyway 11k1 Fixed scroll keyway first side surface 11k2 Fixed scroll keyway second side surface 11k3 Fixed scroll keyway bottom surface 12 Orbiting scroll 12a Orbiting scroll end plate 12b Orbiting spiral wrap 12c Boss section 12k Orbiting scroll keyway 12k1 Orbiting scroll keyway first side surface 12k2 Orbiting scroll keyway second side surface 12k3 Orbiting scroll keyway bottom surface 13 Rotating shaft 13a Eccentric shaft DESCRIPTION OF SYMBOLS 13b Lower end 13c Rotating shaft oil supply hole 13d Swivel bearing 13e Oil groove 14 Discharge port 15 Compression chamber 15a Suction port 17 Oldham ring 17k Oldham ring key 18 Sub-bearing 20 Electric mechanism 21 Stator 22 Rotor 30 Main bearing 31 Bearing portion 32 Boss accommodating portion 33 Seal member 51 First oil inlet hole 51s Sub-first oil inlet hole 52 First oil outlet hole 53 First oil communicating passage 54 Oil supply path 61 Second oil inlet hole 61s Sub-second oil inlet hole 62 Second oil outlet hole 63 Second oil communicating passage 64 Oil drain path 100 Scroll compressor 111 Condenser 112 Pressure reducing device 113 Evaporator (C) Substantially enclosed space (D) Outlet (opening position) (H) High pressure region (M) Intermediate pressure region (X) Direction in which the Oldham ring moves (Y) Direction in which the Oldham ring moves

Claims

1. A compressor comprising a compression mechanism for compressing a refrigerant, an electric mechanism for driving the compression mechanism, and a sealed container accommodating the compression mechanism and the electric mechanism, wherein the compression mechanism has a fixed scroll, an orbiting scroll, and a rotation shaft for orbiting the orbiting scroll, wherein the fixed scroll comprises a disk-shaped fixed scroll end plate and a fixed spiral wrap erected on the fixed scroll end plate, and wherein the orbiting scroll comprises a disk-shaped orbiting scroll end plate and an orbiting spiral wrap erected on the wrap-side end face of the orbiting scroll end plate, and the fixed spiral wrap and the orbiting spiral wrap are intermeshed to form a plurality of compression chambers between the fixed spiral wrap and the orbiting spiral wrap, wherein the fixed scroll is fixed to a main bearing at its outer peripheral wall using a plurality of bolts, and wherein Oldham ring keys are arranged on an Oldham ring so as to face each other at right angles on the circumference, the Oldham ring key slides along the orbiting scroll keyway and the fixed scroll keyway provided on the orbiting scroll, the Oldham ring restricts the rotation of the orbiting scroll relative to the fixed scroll, so that the orbiting scroll orbits without rotating relative to the fixed scroll as the rotating shaft rotates with a crank, an intermediate pressure region into which intermediate pressure is introduced is formed on the opposite wrap surface of the orbiting scroll end plate, and the orbiting scroll is pressed against the fixed scroll by the difference between the pressure on the opposite wrap surface of the orbiting scroll end plate and the pressure in the compression chamber, the scroll compressor characterized in that: the fixed scroll is formed with an oil discharge path for discharging oil from the intermediate pressure region to the compression chamber, the pressure of which is lower than that of the intermediate pressure region, and an oil introduction hole for introducing the oil in the intermediate pressure region into the oil discharge path is formed in the fixed scroll keyway.

2. The scroll compressor according to claim 1, wherein the fixed scroll keyway is composed of a pair of fixed scroll keyway first side surfaces, a pair of fixed scroll keyway second side surfaces, and a fixed scroll keyway bottom surface, the pair of fixed scroll keyway first side surfaces and the fixed scroll keyway bottom surface are formed by surfaces parallel to the direction in which the Oldham ring moves relative to the fixed scroll, the pair of fixed scroll keyway first side surfaces are formed by opposing parallel surfaces, the pair of fixed scroll keyway second side surfaces are formed by opposing parallel surfaces, the fixed scroll keyway bottom surface is formed by a surface perpendicular to the fixed scroll keyway first side surface and is formed between the pair of fixed scroll keyway first side surfaces, the fixed scroll keyway bottom surface is formed by a surface perpendicular to the fixed scroll keyway second side surface and is formed between the pair of fixed scroll keyway second side surfaces, and the oil introduction hole is formed in the pair of fixed scroll keyway second side surfaces or the fixed scroll keyway bottom surface.

3. A scroll compressor according to claim 1, characterized in that an oil communication groove is formed in the fixed scroll, the oil in a high-pressure region having a higher pressure than the intermediate-pressure region is intermittently supplied to the oil communication groove, and the oil supplied to the oil communication groove is supplied only to the fixed scroll keyway that is different from the fixed scroll keyway.

4. A scroll compressor as described in claim 3, characterized in that an oil supply passage is formed in the orbiting scroll, and a first oil outlet hole serving as an outlet of the oil supply passage intermittently communicates with the oil communication groove as the rotating shaft rotates with a crank.

5. A refrigeration cycle device using the scroll compressor according to any one of claims 1 to 4, characterized in that the scroll compressor, a condenser, a pressure reducing device, and an evaporator are connected in a circular configuration by refrigerant piping.

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