Scroll compressor

Abstract

A scroll compressor according to the present disclosure comprises: a casing; a rotary shaft extending in the vertical direction within the casing; a bearing supporting the rotary shaft so as to be rotatable around an axis; a compression part having an orbiting scroll connected to the rotary shaft above the bearing and a fixed scroll meshing with the orbiting scroll from above to form a compression chamber inside; an oil supply mechanism supplying lubricating oil to a machine chamber defined between the bearing and the orbiting scroll; and a seal part sealing the orbiting scroll and the fixed scroll. The orbiting scroll has an orbiting end plate and an orbiting wrap. The fixed scroll has a fixed end plate and a fixed wrap. The orbiting end plate is provided with a recessed groove part. The groove part is located on the upper surface of the orbiting end plate at a position radially inward from the seal part.

Description

Scroll compressor

[0001] The present disclosure relates to a scroll compressor. The present application claims priority based on Japanese Patent Application No. 2025-039005 filed in Japan on March 12, 2025, and incorporates the content thereof herein by reference.

[0002] Patent Document 1 discloses a scroll compressor. The scroll compressor includes a casing, a compression unit, and a seal portion. The casing accommodates a rotating shaft, a drive unit, the compression unit, and a main bearing that supports the upper end of the rotating shaft, and stores lubricating oil therein. The compression unit includes a movable scroll and a fixed scroll. A compression chamber that compresses refrigerant is formed between the movable scroll and the fixed scroll. Further, the seal portion seals fluid flow between the inside and the outside of the compression unit within the casing.

[0003] Japanese Unexamined Patent Publication No. 2020-51406

[0004] Incidentally, lubricating oil is sealed in the casing to lubricate sliding parts, and the smaller the discharge amount of lubricating oil from the compression unit (oil discharge amount) is, the lower the frequency of oil return operation can be, which improves usability. For this reason, in the scroll compressor of Patent Document 1, the above-described seal portion is provided to prevent excessive supply of lubricating oil to the compression unit. However, when the supply amount of lubricating oil into the compression unit is extremely reduced, for example, immediately after operating a scroll compressor that has been stopped for a long time, there is a risk that lubrication in the compression unit and the seal portion may not be properly performed.

[0005] Additionally, recent air-conditioning compressors tend to use refrigerants with low GWP (Global Warming Potential). However, many low-GWP refrigerants are less likely to provide sufficient cooling capacity, so increasing capacity and rotation speed become essential to achieve the same performance as the required refrigerant capacity. When realizing higher capacity and higher rotation speed in a scroll compressor, if the movable scroll is heavy, the shaft system cannot be balanced, which leads to vibration and noise, and also increases bearing load. Further, for example, the movable scroll of the scroll compressor described in Patent Document 1 has a round end plate shape due to the provision of an annular seal portion, which has a problem of easily increasing weight.

[0006] This disclosure was made to solve the above-mentioned problems and aims to provide a scroll compressor that can achieve weight reduction while ensuring lubricity of the compression section.

[0007] To solve the above problems, the scroll compressor according to this disclosure includes a casing, a rotating shaft having an eccentric shaft centered on an axis extending vertically within the casing and having an eccentric axis at its upper end centered on an eccentric axis extending parallel to the axis, a bearing that supports the rotating shaft so as to be rotatable around the axis and divides the inside of the casing vertically, a movable scroll connected to the rotating shaft above the bearing and capable of eccentric rotation around the axis as the rotating shaft rotates, and a fixed scroll that meshes with the movable scroll from above to form a compression chamber on the inside and has an intake port for drawing in refrigerant from an intake chamber outside the compression chamber, and a compression section having a fixed scroll that meshes with the movable scroll from above to form a compression chamber on the inside and has an intake port for drawing in refrigerant from an intake chamber outside the compression chamber, and a storage area below the bearing within the casing The system includes a lubrication mechanism that supplies lubricated lubricant to a machine chamber partitioned between the bearing and the movable scroll, and a sealing portion provided between the movable scroll and the fixed scroll to seal the movable scroll and the fixed scroll, wherein the movable scroll has a movable end plate connected to the rotating shaft and a movable lap protruding upward from the movable end plate, and the fixed scroll has a fixed end plate positioned above the movable end plate and facing the movable end plate in the vertical direction, and a fixed lap that is discharged downward from the fixed end plate and housed between the movable laps, wherein the movable end plate is provided with a recessed groove, and the groove is provided on the upper surface of the movable end plate on the inner circumference side of the sealing portion.

[0008] The scroll compressor of this disclosure makes it possible to achieve weight reduction while ensuring lubricity of the compression section.

[0009] This is a configuration diagram of a scroll compressor according to an embodiment of the present disclosure. This is an enlarged view of the area around the compression section according to an embodiment of the present disclosure. This is a top view of the movable scroll according to an embodiment of the present disclosure. This is a bottom view of the movable scroll according to an embodiment of the present disclosure. This is a cross-sectional view along the line V-V in Figure 3 according to an embodiment of the present disclosure. This is a bottom view of a movable scroll according to a modified example of the present disclosure.

[0010] (Configuration of the scroll compressor) Hereinafter, a scroll compressor 1 according to an embodiment of the present disclosure will be described with reference to Figures 1 to 5. As shown in Figures 1 and 2, the scroll compressor 1 comprises a casing 2, a rotating shaft 3, a main bearing 4 (bearing), a sub-bearing 5, a drive unit 6, a compression unit 7, a coupling 8, a balance weight 9, a thrust bearing 10, an Oldham ring 11, a seal unit 12, a discharge valve mechanism 13, and a lubrication mechanism 14.

[0011] (Casing) The casing 2 extends vertically. The casing 2 is provided with an intake pipe 15 and a discharge pipe 16. The intake pipe 15 draws refrigerant R from outside the casing 2 into the upper space above the main bearing 4, which will be described later, inside the casing 2. The intake pipe 15 is located at the top of the casing 2. The intake pipe 15 is located opposite the compression section 7 in a direction perpendicular to the axis O1. The discharge pipe 16 discharges the refrigerant R, which has become high-pressure after being compressed by the compression section 7. The discharge pipe 16 is located at the top of the casing 2, above the intake pipe 15. Lubricating oil L (refrigerant oil) is stored at the bottom of the casing 2.

[0012] (Rotation Axis) The rotation axis 3 is located inside the casing 2. The rotation axis 3 is formed in a cylindrical shape with axis O1 as the axis. In this embodiment, axis O1 extends in the vertical direction. Hereafter, unless otherwise specified, "axial direction" means the direction in which axis O1 of the rotation axis 3 extends, "radial direction" means the radial direction of axis O1, and "circumferential direction" means the circumferential direction of axis O1.

[0013] The rotating shaft 3 is supported within the casing 2 by a main bearing 4 and a sub-bearing 5, which will be described later, so as to be rotatable around the axis O1. An eccentric shaft 3a is provided at the upper end of the rotating shaft 3. The eccentric shaft 3a is located at a position a distance of a turning radius r from the axis O1. The eccentric shaft 3a is formed in a columnar shape with an eccentric axis O2, which is different from the axis O1, as its center. The eccentric axis O2 extends parallel to the axis O1. When the rotating shaft 3 is rotating around the axis O1, the eccentric shaft 3a revolves around the axis O1 of the rotating shaft 3.

[0014] (Main Bearing) The main bearing 4 supports the upper end of the rotating shaft 3 so that it can rotate around the axis O1. The outer surface of the main bearing 4 is fixed by welding or interference fit, etc., in contact with the inner surface of the casing 2 over its entire circumference. The main bearing 4 divides the space inside the casing 2 into upper and lower sections. The lower space inside the casing 2 below the main bearing 4 is the drive chamber V1 which houses the drive unit 6. The upper space inside the casing 2 above the main bearing 4 houses the compression unit 7. This upper space is divided into the machine chamber V2, which will be described later, the intake chamber V3, and the discharge chamber V4.

[0015] The main bearing 4 comprises a bearing lower part 4a, a bearing end plate 4b, and a bearing outer cylinder portion 4c. The bearing lower part 4a is provided to cover the upper end of the rotating shaft 3 from the outer circumference. The bearing end plate 4b is provided above the bearing lower part 4a and is formed in a disc shape that extends horizontally. A balance weight chamber 4d is formed in the center of the bearing end plate 4b. The balance weight chamber 4d houses a balance weight 9 that is attached to the eccentric shaft 3a. The bearing outer cylinder portion 4c is formed to rise upward along the entire circumference of the outer edge of the bearing end plate 4b. The outer circumferential surface of the bearing end plate 4b and the outer circumferential surface of the bearing outer cylinder portion 4c are fixed to the inner circumferential surface of the casing 2.

[0016] Furthermore, as shown in Figure 2, a machine chamber V2 is formed between the main bearing 4 and the movable scroll 20, which will be described later. The machine chamber V2 is partitioned not only by the main bearing 4 and the movable scroll 20, but also by the fixed scroll 21, which will be described later. The machine chamber V2 houses movable members such as the eccentric shaft 3a, the coupling 8, balance weight 9, thrust bearing 10, and Oldham ring 11, which will be described later. When the compression section 7 is driven, the lubricating oil L stored in the drive chamber V1 is guided to the machine chamber V2 by the lubrication mechanism 14, which will be described later. In addition, a through hole 4e is formed on the outer peripheral edge of the bearing end plate 4b, inside the bearing outer cylinder 4c. The through hole 4e penetrates the bearing end plate 4b in the axial direction. The through hole 4e returns the lubricating oil L supplied to the machine chamber V2 back to the drive chamber V1.

[0017] (Sub-bearing) The sub-bearing 5 rotatably supports the lower end of the rotating shaft 3. The sub-bearing 5 is fixed to the inner circumferential surface of the casing 2.

[0018] (Drive Unit) The drive unit 6 is an electric motor located in the drive chamber V1 inside the casing 2. The drive unit 6 rotates the rotating shaft 3.

[0019] (Compression section) The compression section 7 is connected to the drive section 6 by a rotating shaft 3. The compression section 7 compresses the refrigerant R by being driven by the rotation of the rotating shaft 3. The compression section 7 includes a movable scroll 20, a fixed scroll 21, and a discharge cover 22.

[0020] (Movable Scroll) The movable scroll 20 is connected to the rotating shaft 3 above the main bearing 4. The movable scroll 20 has a movable end plate 20a and a movable lap 20b. The movable end plate 20a is connected to the eccentric shaft 3a of the rotating shaft 3. The movable end plate 20a is formed in the shape of a disc extending in the horizontal direction. The movable end plate 20a is attached to the eccentric shaft 3a such that the central axis O3 of the movable end plate 20a is approximately parallel to the eccentric axis O2 of the eccentric shaft 3a. The movable lap 20b protrudes upward from the upper surface of the movable end plate 20a and is formed in the shape of a spiral. A movable side tip seal 20b1 (see Figure 3) is provided along the tip edge (tooth tip) of the movable lap 20b. A boss 23 is integrally provided on the lower surface of the movable end plate 20a. The eccentric shaft 3a is fitted into the boss 23 via a coupling 8 which will be described later. As a result, when the rotating shaft 3 rotates, the movable scroll 20 revolves around the axis O1 without rotating on its own axis. In this way, the movable scroll 20 is made capable of eccentric rotation around the axis O1 in conjunction with the rotation of the rotating shaft 3. Furthermore, an annular seal groove 20c is formed radially outward of the movable end plate 20a from the movable lap 20b. In addition, a groove 50 is formed in the movable end plate 20a. The location and shape of the groove 50 will be described in detail later.

[0021] (Fixed Scroll) The fixed scroll 21 is provided to engage with the movable scroll 20 from above. When the fixed scroll 21 and the movable scroll 20 engage, a volume-variable compression chamber V5 is formed inside the fixed scroll 21. The fixed scroll 21 has a fixed end plate 21a, a fixed wrap 21b, and a fixed outer cylinder portion 21c. The fixed end plate 21a is positioned above the movable end plate 20a and is positioned opposite the movable end plate 20a in the vertical direction. The fixed end plate 21a is formed in the shape of a disc extending horizontally. A discharge port 24 is formed in the center of the fixed end plate 21a, penetrating in the axial direction. The discharge port 24 discharges the refrigerant R compressed in the compression chamber V5. The fixed wrap 21b protrudes downward from the lower surface of the fixed end plate 21a and is formed in a spiral shape. The fixed wrap 21b is housed between the movable wraps 20b. The fixed lap 21b, like the movable lap 20b, is also provided with a fixed-side tip seal (not shown) along its leading edge (tooth tip). The fixed outer cylinder portion 21c is formed to rise downward from the outer peripheral edge of the fixed end plate 21a. The fixed outer cylinder portion 21c surrounds the fixed lap 21b from the outer peripheral side. The fixed outer cylinder portion 21c is formed to cover the fixed lap 21b and the movable lap 20b from the outer peripheral side. The fixed outer cylinder portion 21c is fitted into the casing 2 and abuts against the bearing outer cylinder portion 4c of the main bearing 4. The fixed outer cylinder portion 21c is fixed to the bearing outer cylinder portion 4c by bolts 25. An intake chamber V3 is formed on the outer peripheral side of the fixed outer cylinder portion 21c. That is, the intake chamber V3 is formed outside the compression chamber V5. The intake chamber V3 is partitioned by the fixed scroll 21 and the discharge cover 22, which will be described later. The intake chamber V3 is connected to an intake pipe 15, through which refrigerant R is introduced from outside the casing 2. An intake port 21d is formed in the fixed outer cylinder portion 21c, penetrating radially. The intake port 21d draws refrigerant R from the intake chamber V3 into the compression chamber V5. The compression chamber V5 moves to the center of the compression section 7, decreasing in volume due to the eccentric movement of the movable scroll 20. This compresses the refrigerant R in the compression chamber V5. The refrigerant R compressed in the compression chamber V5 is discharged from the discharge port 24.

[0022] (Discharge Cover) The discharge cover 22 is positioned above the fixed scroll 21. The discharge cover 22 is formed in a horizontally extending disc shape. A discharge port 26 is formed in the center of the discharge cover 22. The discharge cover 22 further divides the upper space above the main bearing 4 within the casing 2 vertically. The space above the discharge cover 22, which is divided by the discharge cover 22, is designated as the discharge chamber V4. An intermediate chamber V6 is also formed between the discharge cover 22 and the fixed scroll 21. Refrigerant R discharged from the compression chamber V5 flows into the intermediate chamber V6 through the discharge port 24. Refrigerant R discharged from the intermediate chamber V6 flows into the discharge chamber V4 through the discharge port 26. The discharge piping 16 described above is connected to the discharge chamber V4. The refrigerant R in the discharge chamber V4 is discharged outside the casing 2 through the discharge piping 16.

[0023] (Coupling) The coupling 8 is a cylindrical member fitted onto the outer surface of the eccentric shaft 3a. The coupling 8 is located within the boss 23 of the movable scroll 20. As the eccentric shaft 3a rotates around the axis O1, the rotational force is transmitted to the movable scroll 20 through the coupling 8. The coupling 8 is also referred to as a drive bush.

[0024] (Balance weight) The balance weight 9 is attached to the eccentric shaft 3a via the coupling 8. The balance weight 9 balances the weight of the movable scroll 20, which is mounted eccentrically with respect to the rotating shaft 3.

[0025] (Thrust bearing) The thrust bearing 10 is provided between the movable end plate 20a of the movable scroll 20 and the bearing end plate 4b of the main bearing 4. The thrust bearing 10 supports the axial load applied to the compression section 7 and the rotating shaft 3.

[0026] (Oldham Ring) The Oldham ring 11 is located between the movable scroll 20 and the bearing end plate 4b of the main bearing 4, and is provided on the outer circumference side of the thrust bearing 10. The Oldham ring 11 restricts the rotation of the movable scroll 20 (rotation around the eccentric axis O2). The Oldham ring 11 has a ring body 11a and a key 30. The key 30 is provided on the upper and lower surfaces of the ring body 11a. The key 30 formed on the lower surface of the ring body 11a is called the first key 31, and the key 30 formed on the upper surface of the ring body 11a is called the second key 32. Two first keys 31 are provided so as to face each other in the radial direction of the Oldham ring 11. Also, two second keys 32 are provided so as to face each other in the radial direction of the Oldham ring 11. The main bearing 4 and the movable scroll 20 each have a keyway 40 formed therein that is slidably engaged with the key 30. The keyway 40 formed on the upper surface of the bearing end plate 4b of the main bearing 4 is referred to as the first keyway 41, and the keyway 40 formed on the lower surface of the movable end plate 20a of the movable scroll 20 is referred to as the second keyway 42. The first key 31 is radially slidably engaged with the first keyway 41, and the second key 32 is radially slidably engaged with the second keyway 42. Two first keyways 41 are provided facing each other in the radial direction. Two second keyways 42 are provided facing each other in the radial direction.

[0027] (Sealing section) The sealing section 12 is provided between the fixed scroll 21 and the movable scroll 20. The sealing section 12 is fitted into the sealing groove 20c of the movable scroll 20. The sealing section 12 seals the fixed scroll 21 and the movable scroll 20. More specifically, the sealing section 12 seals the flow of fluid between the inside (compression chamber V5) and the outside of the compression section 7.

[0028] (Discharge valve mechanism) The discharge valve mechanism 13 prevents backflow of the refrigerant R flowing through the discharge ports 24 and 26. The discharge valve mechanism 13 is provided in both the intermediate chamber V6 and the discharge chamber V4. The discharge valve mechanism 13 in the intermediate chamber V6 is attached to the upper surface of the fixed end plate 21a of the fixed scroll 21. The discharge valve mechanism 13 in the discharge chamber V4 is attached to the upper surface of the discharge cover 22.

[0029] (Lubrication Mechanism) The lubrication mechanism 14 supplies lubricating oil L stored below the bearings in the casing 2 to the machine room V2. The lubrication mechanism 14 comprises a lubrication pump 14a and a lubrication path 14b. The lubrication pump 14a is attached to the lower end of the rotating shaft 3. The lubrication pump 14a pumps up the lubricating oil L stored at the bottom of the casing 2. The lubrication path 14b is formed inside the rotating shaft 3 along the axis O1. The lubrication path 14b guides the lubricating oil L pumped up by the lubrication pump 14a to the machine room V2.

[0030] (Grooves of the movable scroll) The grooves 50 are grooves for reducing the weight of the movable scroll 20. The grooves 50 are recessed on the surface of the movable end plate 20a of the movable scroll 20. The grooves 50 are formed on at least the upper surface of the surface of the movable end plate 20a. In this embodiment, the grooves 50 are formed on the upper and lower surfaces of the movable end plate 20a, respectively. The groove 50 formed on the upper surface of the movable end plate 20a is referred to as the compression side groove 51, and the groove 50 formed on the lower surface of the movable end plate 20a is referred to as the bearing side groove 52. The grooves 50 are designed so as not to impair the rigidity required of the movable scroll 20. The location, shape, and number of grooves 50 will be described in detail below.

[0031] (Compression side groove) The compression side groove 51 is provided on the upper surface of the movable end plate 20a on the inner circumference side of the seal groove 20c into which the seal portion 12 is fitted. The compression side groove 51 is formed on the upper surface of the movable end plate 20a in a part that is not the contact portion 20d, which is the area in which the teeth of the fixed lap 21b make contact. The contact portion 20d extends from the outermost edge of the movable lap 20b along the outer circumference of the movable lap 20b in the direction in which the movable lap 20b swirls. The contact portion 20d is a semi-circular region centered on the central axis O3. In addition, both ends of the contact portion 20d overlap the second key groove 42 in the vertical direction. In this embodiment, three compression side grooves 51 are provided so as to surround the movable lap 20b from the outer circumference side. These three compression side grooves 51 are formed at positions along the inner circumference of the seal groove 20c. The three compression grooves 51 are formed to spiral along the outer edge of the contact portion 20d and the outer surface of the movable wrap 20b. Of the three compression grooves 51, the one located furthest to the outermost circumference is referred to as the first compression groove 51a. The compression groove 51 adjacent to the first compression groove 51a in the circumferential direction but extending further inward than the first compression groove 51a is referred to as the second compression groove 51b. The compression groove 51 adjacent to the second compression groove 51b in the circumferential direction but extending further inward than the second compression groove 51b is referred to as the third compression groove 51c. The first compression groove 51a is formed along the outer edge of the contact portion 20d. The second compression groove 51b is formed along the outer surface of the movable wrap 20b. The third compression groove 51c is formed along the outer circumferential surface of the movable lap 20b. The third compression groove 51c is also adjacent to the contact portion 20d in the circumferential direction. The three compression grooves 51 are spaced apart from each other in the circumferential direction, but the circumferential distance between the first compression groove 51a and the third compression groove 51c is the widest. The three compression grooves 51 are also positioned so as not to overlap with the second key grooves 42 in the vertical direction. Specifically, when viewed from above, one second key groove 42 is located between the first compression groove 51a and the second compression groove 51b, and the remaining second key groove 42 is located between the third compression groove 51c and the first compression groove 51a.

[0032] (Bearing side groove) The bearing side groove 52 is provided on the lower surface of the movable end plate 20a in a portion that is not the thrust sliding portion 20e and not the chuck portion 20f. The thrust sliding portion 20e is the portion of the lower surface of the movable end face that is in slidable contact with the thrust bearing 10. The thrust sliding portion 20e is an annular area surrounding the boss 23. The chuck portion 20f is the portion that is held when the movable scroll 20 is being machined. The chuck portion 20f is provided, for example, on the outer peripheral edge of the lower surface of the movable end plate 20a. In the illustrated example, three are provided in a circumferential direction. The chuck portions 20f are provided in positions that avoid the two second keyways 42. In this embodiment, the bearing side groove 52 is provided on the inside of the boss 23. The bearing side groove 52 is formed in a circular shape when viewed from below, and the outer peripheral edge of the bearing side groove 52 is formed to follow the inner circumferential surface of the boss 23.

[0033] Furthermore, these grooves 50 are formed such that the distance between the axis O1 and the center of gravity P of the movable scroll 20 is less than or equal to the rotation radius r, which is the distance between the axis O1 and the eccentric axis O2 (see Figure 2).

[0034] (Effects) According to this embodiment, the following effects are achieved.

[0035] In this embodiment, the movable end plate 20a is provided with a recessed groove 50. The groove 50 is located on the upper surface of the movable end plate 20a, on the inner side of the seal portion 12.

[0036] The groove 50 functions as an oil reservoir for storing lubricating oil L. Since this groove 50 is located on the inner circumference side of the seal 12, this configuration allows lubricating oil L to be stored inside the compression section 7. Therefore, even if the supply of lubricating oil L to the compression section 7 is drastically reduced, the lubricity of the compression section 7 can be ensured.

[0037] Incidentally, due to the need to provide an annular seal portion 12, there is a concern that the movable scroll 20 will become larger in the radial direction and its weight will increase. However, by providing a groove portion 50 as in this embodiment, the movable scroll 20 is lightened. Therefore, weight reduction can be achieved. This makes it easier to adjust the axial balance and reduces the bearing load. Furthermore, it leads to miniaturization of balance adjustment parts, thus reducing manufacturing costs. In addition, it leads to a reduction in the shaft diameter of the rotating shaft 3, so the scroll compressor 1 can be operated with less power and high efficiency can be achieved.

[0038] In this embodiment, it is provided on the upper surface of the movable end plate 20a in a portion that is not the contact portion 20d that the teeth of the fixed lap 21b make contact with.

[0039] If a groove 50 is formed in the contact portion 20d with the tooth tip of the fixed lap 21b, the refrigerant R will separate inside the compression chamber V5. In this embodiment, since the groove 50 is formed in a portion other than the contact portion 20d, the separation of the refrigerant R inside the compression chamber V5 is suppressed. Therefore, the groove 50 can be formed without suppressing performance degradation.

[0040] In this embodiment, the groove 50 is provided on the upper surface of the movable end plate 20a in a portion that does not overlap with the keyway 40 in the vertical direction.

[0041] The groove 50 is formed while avoiding the area where the keyway 40 is formed, which is thinner than other parts. As a result, the upper part of the keyway 40 does not become excessively thin, and the groove 50 can be formed without reducing rigidity.

[0042] In this embodiment, the groove 50 is provided on the upper surface of the movable end plate 20a, and also on the lower surface of the movable end plate 20a, specifically on the portion that does not slide against the thrust bearing 10 (the thrust sliding portion 20e).

[0043] The groove 50 can also be formed on the lower surface of the movable end plate 20a. This allows further weight reduction of the orbiting scroll 20. Furthermore, the groove 50 on the lower surface of the movable end plate 20a is formed avoiding the thrust sliding portion 20e. Therefore, the groove 50 can also be formed on the lower surface of the movable end plate 20a without impairing stability.

[0044] In the present embodiment, the groove 50 is provided on the upper surface of the movable end plate 20a, and is also provided in a portion that is not the chuck portion 20f on the lower surface of the movable end plate 20a.

[0045] The groove 50 can also be formed on the lower surface of the movable end plate 20a. This allows further weight reduction of the orbiting scroll 20. Furthermore, the groove 50 on the lower surface of the movable end plate 20a is formed avoiding the chuck portion 20f that is held during processing. Therefore, the groove 50 can also be formed on the lower surface of the movable end plate 20a without impairing workability.

[0046] In the present embodiment, the distance between the axis O1 and the center of gravity P of the orbiting scroll 20 is equal to or less than the turning radius r, which is the distance between the axis O1 and the eccentric axis O2.

[0047] This makes it possible to reduce whirling of the orbiting scroll 20.

[0048] (Modified Example) Next, a modified example will be described with reference to FIG. 6. As shown in FIG. 6, the bearing-side groove 52 may be provided, in addition to the inner side of the boss portion 23, on the outer peripheral edge of the movable end plate 20a and between the chuck portions 20f. The bearing-side groove 52 provided between the chuck portions 20f extends along the outer peripheral edge of the movable end plate 20a. Furthermore, the bearing-side groove 52 provided between the chuck portions 20f is formed so as to avoid the second key groove 42. Forming the bearing-side groove 52 in this manner increases the material removal of the orbiting scroll 20 without impairing the rigidity of the orbiting scroll 20, allowing further weight reduction of the orbiting scroll 20.

[0049] (Other Embodiments) Although the embodiments of the present disclosure have been described in detail with reference to the drawings above, the specific configuration is not limited to these embodiments, and design changes and the like within a scope that does not deviate from the gist of the present disclosure are also included.

[0050] <Note> The scroll compressor 1 described in each embodiment can be understood, for example, as follows.

[0051] (1) The scroll compressor 1 according to the first embodiment includes a casing 2, a rotating shaft 3 centered on an axis O1 extending vertically within the casing 2 and having an eccentric shaft 3a at its upper end centered on an eccentric axis O2 extending parallel to the axis O1, a bearing that supports the rotating shaft 3 so as to be rotatable around the axis O1 and divides the inside of the casing 2 vertically, a movable scroll 20 connected to the rotating shaft 3 above the bearing and capable of eccentric rotation around the axis O1 as the rotating shaft 3 rotates, and a fixed scroll 21 that meshes with the movable scroll 20 from above to form a compression chamber V5 on its inside and has an intake port 21d for drawing in refrigerant R from an intake chamber V3 outside the compression chamber V5, and a compression section 7 having lubricating oil L stored below the bearing in the casing 2, and the bearing and the movable The system includes a lubrication mechanism 14 that supplies oil to a machine chamber V2 partitioned between the movable scroll 20 and the fixed scroll 21, and a seal portion 12 provided between the movable scroll 20 and the fixed scroll 21 to seal the movable scroll 20 and the fixed scroll 21. The movable scroll 20 has a movable end plate 20a connected to the rotating shaft 3 and a movable wrap 20b protruding upward from the movable end plate 20a. The fixed scroll 21 has a fixed end plate 21a positioned above the movable end plate 20a and facing the movable end plate 20a in the vertical direction, and a fixed wrap 21b that is discharged downward from the fixed end plate 21a and housed between the movable wraps 20b. The movable end plate 20a is provided with a recessed groove 50, and the groove 50 is provided on the upper surface of the movable end plate 20a on the inner circumference side of the seal portion 12. An example of a bearing is the main bearing 4 of the above-described embodiment.

[0052] The groove 50 functions as an oil reservoir for storing lubricating oil L. Since the groove 50 is located on the inner circumference side of the seal 12, this configuration allows lubricating oil L to be stored inside the compression section 7. Therefore, even if the supply of lubricating oil L to the compression section 7 is drastically reduced, the lubricity of the compression section 7 can be ensured. In addition, the movable scroll 20 is lightened by the groove 50. Therefore, weight reduction can be achieved.

[0053] (2) The scroll compressor 1 of the second embodiment is the scroll compressor 1 of (1), wherein the groove 50 may be provided on the upper surface of the movable end plate 20a in a part other than the contact portion 20d in which the tooth tip of the fixed lap 21b makes contact.

[0054] If a groove 50 is formed in the contact portion 20d with the tooth tip of the fixed lap 21b, the refrigerant R will separate inside the compression chamber V5. In this embodiment, since the groove 50 is formed in a portion other than the contact portion 20d, the separation of the refrigerant R inside the compression chamber V5 is suppressed. Therefore, the groove 50 can be formed without suppressing performance degradation.

[0055] (3) The scroll compressor 1 of the third embodiment is the scroll compressor 1 of (1) or (2), further comprising an Oldham ring 11 provided between the bearing and the movable scroll 20 to restrict the rotation of the movable scroll 20, wherein a keyway 40 is formed on the lower surface of the movable end plate 20a into which the key 30 of the Oldham ring 11 is slidably engaged, and the groove 50 may be provided on the upper surface of the movable end plate 20a in a part that does not overlap with the keyway 40 in the vertical direction.

[0056] The groove 50 is formed while avoiding the area where the keyway 40 is formed, which is thinner than other parts. Therefore, the groove 50 can be formed without reducing rigidity.

[0057] (4) The scroll compressor 1 of the fourth embodiment is any one of the scroll compressors 1 of (1) to (3), further comprising a thrust bearing 10 provided between the movable end plate 20a and the bearing to support a load in the extending direction of the axis O1, wherein the groove 50 is provided on the upper surface of the movable end plate 20a and may also be provided on the lower surface of the movable end plate 20a, except for the thrust sliding portion 20e that slides with the thrust bearing 10.

[0058] A groove 50 can also be formed on the lower surface of the movable end plate 20a. This allows for further weight reduction of the movable scroll 20. Furthermore, the groove 50 on the lower surface of the movable end plate 20a is formed to avoid the thrust sliding portion 20e. Therefore, a groove 50 can be formed on the lower surface of the movable end plate 20a without compromising stability.

[0059] (5) The scroll compressor 1 of the fifth embodiment is any one of the scroll compressors 1 of (1) to (4), wherein the groove 50 is provided on the upper surface of the movable end plate 20a and may also be provided on the lower surface of the movable end plate 20a, except for the chuck portion 20f.

[0060] A groove 50 can also be formed on the lower surface of the movable end plate 20a. This allows for further weight reduction of the movable scroll 20. Furthermore, the groove 50 on the lower surface of the movable end plate 20a is formed to avoid the chuck portion 20f that is held during processing. Therefore, a groove 50 can be formed on the lower surface of the movable end plate 20a without impairing workability.

[0061] (6) The scroll compressor 1 of the fifth embodiment is any one of the scroll compressors 1 of (1) to (5), wherein the distance between the axis O1 and the center of gravity P of the movable scroll 20 may be less than or equal to the turning radius r, which is the distance between the axis O1 and the eccentric axis O2.

[0062] This reduces the oscillation of the movable scroll 20.

[0063] The scroll compressor of this disclosure makes it possible to achieve weight reduction while ensuring lubricity of the compression section.

[0064] 1 Scroll compressor 2 Casing 3 Rotating shaft 3a Eccentric shaft 4 Main bearing 4a Lower part of bearing 4b Bearing end plate 4c Bearing outer cylinder 4d Balance weight chamber 4e Through hole 5 Sub bearing 6 Drive unit 7 Compression unit 8 Coupling 9 Balance weight 10 Thrust bearing 11 Oldham ring 11a Ring body 12 Seal part 13 Discharge valve mechanism 14 Lubrication mechanism 14a Lubrication pump 14b Lubrication path 15 Suction piping 16 Discharge piping 20 Movable scroll 20a Movable end plate 20b Movable lap 20c Seal groove 20d Contact part 20e Thrust sliding part 20f Chuck part 21 Fixed scroll 21a Fixed end plate 21b Fixed lap 21c Fixed outer cylinder 21d Suction port 22 Discharge cover 23 Boss 24 Discharge port 25 Bolt 26 Discharge port 30 Key 31 First key 32 Second key 40 Keyway 41 First keyway 42 Second keyway 50 Groove 51 Compression side groove 51a First compression side groove 51b Second compression side groove 51c Third compression side groove 52 Bearing side groove L Lubricating oil O1 Axis O2 Eccentric axis O3 Center axis P Center of gravity R Refrigerant V1 Drive chamber V2 Machine chamber V3 Intake chamber V4 Discharge chamber V5 Compression chamber V6 Intermediate chamber

Claims

1. A casing; a rotating shaft having an axis extending vertically within the casing as its center, with an eccentric shaft at its upper end having an eccentric axis extending parallel to the axis as its center; a bearing supporting the rotating shaft so as to be rotatable around the axis and dividing the inside of the casing vertically; a compression section having a movable scroll connected to the rotating shaft above the bearing and capable of eccentric rotation around the axis as the rotating shaft rotates, and a fixed scroll that meshes with the movable scroll from above to form a compression chamber on the inside and has an intake port for drawing in refrigerant from an intake chamber outside the compression chamber; a lubrication mechanism for supplying lubricating oil stored below the bearing within the casing to a machine chamber partitioned between the bearing and the movable scroll; and a sealing section provided between the movable scroll and the fixed scroll to seal the movable scroll and the fixed scroll, wherein the movable scroll has a movable end plate connected to the rotating shaft, A scroll compressor having a movable wrap protruding upward from the movable end plate, the fixed scroll having a fixed end plate positioned above the movable end plate and facing the movable end plate in the vertical direction, and a fixed wrap that is discharged downward from the fixed end plate and housed between the movable wraps, the movable end plate being provided with a recessed groove, the groove being provided on the upper surface of the movable end plate on the inner circumference side of the seal portion.

2. The scroll compressor according to claim 1, wherein the groove is provided on the upper surface of the movable end plate in a portion that is not a contact portion in which the teeth of the fixed lap contact.

3. The scroll compressor according to claim 1 or 2, further comprising an Oldham ring provided between the bearing and the movable scroll to restrict the rotation of the movable scroll, wherein a keyway is formed on the lower surface of the movable end plate into which the key of the Oldham ring is slidably engaged, and the groove is provided on the upper surface of the movable end plate in a portion that does not overlap with the keyway in the vertical direction.

4. The scroll compressor according to claim 1 or 2, further comprising a thrust bearing provided between the movable end plate and the bearing to support a load in the direction of extension of the axis, wherein the groove is provided on the upper surface of the movable end plate and on the lower surface of the movable end plate, in a portion that is not a thrust sliding portion that slides with the thrust bearing.

5. The scroll compressor according to claim 1 or 2, wherein the groove is provided on the upper surface of the movable end plate and on the lower surface of the movable end plate, in a portion other than the chuck portion.

6. The scroll compressor according to claim 1 or 2, wherein the distance between the axis and the center of gravity of the movable scroll is less than or equal to the turning radius, which is the distance between the axis and the eccentric axis.

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