Scroll Compressor

Abstract

To provide a scroll compressor whose lubrication performance is further improved.SOLUTION: A scroll compressor comprises an electric motor, a rotating shaft to be rotated around an axis extending in a horizontal direction, a bearing part for supporting the rotating shaft, a turning scroll to be turned around the axis, a fixed scroll for forming a compression chamber by being opposed to the turning scroll, a rotation prevention mechanism provided in the turning scroll, and an oil supply passage capable of supplying lubricating oil to the rotation prevention mechanism. The rotation prevention mechanism comprises a circular guide concave part formed in a back surface of the turning scroll, and a pin inserted into the guide concave part, and for guiding the turning of the turning scroll by being in contact with an inner peripheral surface of the guide concave part. The oil supply passage comprises a supply hole formed in the bearing part, and to be made to face the guide concave part in association with the turning of the turning scroll.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present disclosure relates to scroll compressors. [Background technology]

[0002] A scroll compressor mainly comprises a fixed scroll fixed to a housing and an orbiting scroll that faces the fixed scroll to form a compression chamber between them. The orbiting scroll orbits at a position eccentric to the rotation axis, so that the volume of the compression chamber changes over time, thereby compressing the refrigerant (for example, see Patent Document 1 below).

[0003] In the field of automobiles, scroll compressors are usually placed horizontally. In other words, the scroll compressor is arranged with the above-mentioned rotation axis facing horizontally. In this case, lubricating oil for lubricating each part is stored in an oil reservoir provided in the lower part of the housing by gravity. It is necessary to supply lubricating oil from the oil reservoir to each part. Examples of parts that require lubrication include bearings, sliding parts between the fixed scroll and the orbiting scroll, and anti-rotation mechanisms. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] JP 2005-351112 A Summary of the Invention [Problem to be solved by the invention]

[0005] However, with the conventional configuration, it is difficult to directly supply lubricating oil to many of the above-mentioned parts, and as a result, the lubricating oil may not reach the desired areas, which may result in a loss of lubricating performance.

[0006] The present disclosure has been made to solve the above-mentioned problems, and has an object to provide a scroll compressor with further improved lubrication performance. [Means for solving the problem]

[0007] In order to solve the above problems, a scroll compressor according to the present disclosure includes an electric motor, a rotating shaft that is driven by the electric motor to rotate about an axis extending in a horizontal direction, a bearing portion supporting the rotating shaft, an orbiting scroll that orbits about the axis as the rotating shaft rotates, a fixed scroll that faces the orbiting scroll from one side in the axial direction to form a compression chamber, a rotation prevention mechanism provided on the orbiting scroll, and an oil supply flow passage capable of supplying lubricating oil to the rotation prevention mechanism, wherein the rotation prevention mechanism has a circular guide recess formed on a back surface of the orbiting scroll facing the other side in the axial direction, and a pin that is fixed to the bearing portion and inserted into the guide recess and abuts against an inner circumferential surface of the guide recess to guide the orbit of the orbiting scroll, and the oil supply flow passage is disposed between the bearing portion and the orbiting scroll. Inside Formed in and has a supply hole opening to one side in the axial direction. , The supply hole is Orbiting of the orbiting scroll Depending on the location, Facing the guide recess The movable scroll is in one of the following states: facing the rear surface of the movable scroll, or exposed to the outer circumferential side of the movable scroll. Effect of the Invention

[0008] According to the present disclosure, it is possible to provide a scroll compressor with further improved lubrication performance. [Brief description of the drawings]

[0009] [Figure 1] 1 is a cross-sectional view showing a configuration of a scroll compressor according to an embodiment of the present disclosure. [Diagram 2] FIG. 2 is an enlarged cross-sectional view of a main portion of a scroll compressor according to an embodiment of the present disclosure. [Diagram 3] FIG. 4 is a plan view of the orbiting scroll according to the embodiment of the present disclosure as viewed from the other axial side. [Figure 4] FIG. 2 is a cross-sectional view showing dimensions of each part according to an embodiment of the present disclosure. [Diagram 5] FIG. 2 is a view of a fixed scroll and a first housing according to an embodiment of the present disclosure, as viewed from one side in the axial direction. [Figure 6] 6 is a cross-sectional view taken along line VI-VI in FIG. 5. [Figure 7] 5 is a cross-sectional view showing a state in which the orbiting scroll according to the embodiment of the present disclosure has been slightly orbited from the state shown in FIG. 4. [Figure 8] 8 is a cross-sectional view showing a state in which the orbiting scroll according to the embodiment of the present disclosure has further orbited from the state shown in FIG. 7. FIG. [Figure 9] 11 is a cross-sectional view illustrating a modified example of a seal portion according to an embodiment of the present disclosure. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0010] (Configuration of scroll compressor) A scroll compressor 100 according to an embodiment of the present disclosure will be described below with reference to Fig. 1 to Fig. 9. The scroll compressor 100 is used to compress a refrigerant for an air conditioner for a vehicle, for example. As shown in Fig. 1, the scroll compressor 100 includes a rotating shaft 1, an electric motor 2, a compressor body 3, a housing 4, a cover 5, an upper bearing 6 (bearing portion), a lower bearing 7, a drive bush 8, and a seal portion 9.

[0011] (Rotation shaft configuration) The rotating shaft 1 extends along an axis O and is rotatable around the axis O. The axis O extends horizontally. That is, the scroll compressor 100 is of a horizontal type. The horizontal direction here refers to a substantially horizontal direction, and manufacturing errors and design tolerances are allowed. The rotating shaft 1 has a rotating shaft main body 10, a small diameter portion 11, a large diameter portion 12, and an eccentric shaft portion 13. The rotating shaft main body 10 is cylindrical with the axis O as its center. The rotating shaft main body 10 has a uniform diameter dimension over the entire area in the direction of the axis O. A rotor 21 (described later) of the electric motor 2 is attached to the outer circumferential surface of the rotating shaft main body 10.

[0012] A small diameter portion 11 is provided on one side (lower side) of the rotating shaft body 10 in the direction of the axis O. The small diameter portion 11 is cylindrical and centered on the axis O, and has a smaller diameter dimension than the rotating shaft body 10. The small diameter portion 11 is supported from one side (lower side) in the direction of the axis O by a lower bearing 7 attached to the housing 4.

[0013] A large diameter portion 12 is provided on the other side (upper side) of the rotating shaft body 10 in the direction of the axis O. The large diameter portion 12 is cylindrical and centered on the axis O, and has a larger diameter dimension than the rotating shaft body 10. The large diameter portion 12 is supported in the radial direction by an upper bearing 6 fixed to the housing 4. The upper bearing 6 has a bearing body 60 and a bearing support portion 61. The bearing body 60 is a journal bearing. The bearing support portion 61 is disk-shaped and centered on the axis O, and is fixed to the inner circumferential surface of the housing 4.

[0014] An eccentric shaft portion 13 is provided further above the large diameter portion 12 (the other side in the direction of the axis O). The eccentric shaft portion 13 protrudes from the large diameter portion 12 toward the other side in the direction of the axis O. The eccentric shaft portion 13 is parallel to the axis O and has a cylindrical shape centered on an eccentric axis A that extends at a position radially shifted from the axis O. Therefore, when the rotating shaft 1 rotates, the eccentric shaft portion 13 revolves (orbits) around the axis O.

[0015] (Motor configuration) The electric motor 2 applies a rotational driving force to the rotating shaft 1. The electric motor 2 has a rotor 21 and a stator 22. The rotor 21 is fixed to the rotating shaft main body 10. The rotor 21 is cylindrical with the axis O as the center. Although not shown in detail, the rotor 21 has a plurality of magnets. The stator 22 covers the rotor 21 from the outer periphery. The stator 22 is formed by stacking a plurality of steel plates in the direction of the axis O and further winding a copper wire thereon (forming a coil). By passing a current through the stator 22, an electromagnetic force is generated between the stator 22 and the rotor 21, and a rotational force about the axis O is applied to the rotor 21. This causes the rotating shaft 1 to rotate about the axis O.

[0016] (Configuration of the Compressor Body) The compressor body 3 is driven by the rotation of the rotary shaft 1 by the electric motor 2. The compressor body 3 has a fixed scroll 31, an orbiting scroll 32, a rotation prevention mechanism 50, and an oil supply passage 92. The fixed scroll 31 has a disk-shaped first end plate 31a centered on the axis O, and a first spiral plate 31b provided on one side (lower side) of the first end plate 31a in the direction of the axis O. The first spiral plate 31b extends in a spiral shape centered on the axis O. The fixed scroll 31 is fixed to the housing 4.

[0017] The orbiting scroll 32 has a disk-shaped second end plate 32a, a second spiral plate 32b provided on the other side (upper side) of the second end plate 32a in the direction of the axis O, and a boss portion 32c. The second spiral plate 32b extends in a spiral shape centered on the axis O. The dimension of the second spiral plate 32b in the direction of the axis O is equal to the dimension of the first spiral plate 31b in the direction of the axis O. In this manner, the first spiral plate 31b and the second spiral plate 32b mesh with each other from the direction of the axis O, thereby forming a compression chamber between them.

[0018] The boss portion 32c is a cylindrical portion that protrudes from the second end plate 32a toward one side (downward) in the direction of the axis O. The boss portion 32c is attached to the eccentric shaft portion 13 of the rotating shaft 1 via a drive bush 8. When the eccentric shaft portion 13 revolves around the axis O, a revolving force is transmitted to the revolving scroll 32 through the drive bush 8. As a result, the revolving scroll 32 revolves around the axis O.

[0019] The rotation (rotation) of the orbiting scroll 32 itself is restricted by a rotation prevention mechanism 50. As shown in Fig. 3, the rotation prevention mechanism 50 has a pin 51, a guide recess 52, and a ring 53. The pin 51 is fixed to a surface of the bearing support part 61 facing one side in the direction of the axis O. The pin 51 protrudes from the bearing support part 61 to one side in the direction of the axis O. A plurality of pins 51 (six, for example) are arranged at intervals in the circumferential direction of the axis O. The guide recess 52 is formed in a back surface 32s (surface facing the other side in the direction of the axis O) of the second end plate 32a of the orbiting scroll 32.

[0020] A plurality of guide recesses 52 (six in one example) are formed on the back surface 32s at intervals in the circumferential direction of the eccentric axis A. The guide recesses 52 are circular when viewed from the axis O direction, and are recessed toward one side in the axis O direction. One pin 51 is inserted into each guide recess 52. An annular ring 53 is attached to the inner periphery of the guide recess 52. The inner periphery surface (ring 53) of the guide recess 52 makes a circular motion while abutting against the pin 51, which enables the orbiting scroll 32 to orbit around the axis O without rotating on its own axis.

[0021] As the orbiting scroll 32 orbits, the volume of the compression chamber changes over time, and the refrigerant is compressed as it is sent from the outside to the inside in the radial direction of the compression chamber, and the pressure of the refrigerant increases. The high-pressure refrigerant is guided into the housing 4 through an opening H formed in the first end plate 31a of the fixed scroll 31.

[0022] As shown in FIG. 1, the housing 4 includes a first housing 4a that houses the electric motor 2 and the compressor body 3, a second housing 4b that is provided on one side of the first housing 4a in the direction of the axis O to cover the fixed scroll 31, and a cover 5 that is integral with the first housing 4a and houses electrical components. As shown in FIG. 2, a partition wall 46 that protrudes toward the other side in the direction of the axis O is provided inside the second housing 4b. The partition wall 46 divides the internal space of the second housing 4b into a high-pressure chamber 45 and an oil reservoir 41. An oil separator 44 is attached to the boundary between the high-pressure chamber 45 and the oil reservoir 41 to separate the lubricating oil contained in the high-pressure refrigerant. The lubricating oil separated by the oil separator 44 is stored in the oil reservoir 41 by gravity.

[0023] An introduction flow passage 42 for introducing the lubricating oil is formed at the bottom of the oil reservoir 41. The introduction flow passage 42 extends in the direction of the axis O. The downstream end of the introduction flow passage 42 opens on a surface (housing end surface 4s) of the second housing 4b facing the other side in the direction of the axis O. A pressure reducing mechanism 43 is inserted inside the introduction flow passage 42. The pressure reducing mechanism 43 is a narrow flow passage formed between parts such as a spiral pin, an orifice, a capillary, etc. The supply pressure of the lubricating oil decreases by passing through the pressure reducing mechanism 43.

[0024] A pair of seal portions 9 form an annular passage 91 in the first end plate 31a of the fixed scroll 31. As shown in FIG. 5 and FIG. 6, an annular groove 31r is formed around the axis O in a surface (main surface 31s) of the first end plate 31a facing one side in the axis O direction. A pair of seal portions 9 (an outer circumferential seal portion 9a and an inner circumferential seal portion 9b) having different diameters are arranged in the groove 31r at a radial interval. As an example, the outer circumferential seal portion 9a is a gasket having a rectangular cross-sectional shape. The inner circumferential seal portion 9b is an O-ring having a circular cross-sectional shape. Each seal portion 9 forms an annular shape around the axis O. The space between these seal portions 9 is the annular passage 91. The lowest part of the annular passage 91 communicates with the introduction passage 42. The lubricating oil introduced into the annular passage 91 through the introduction passage 42 flows upward in the circumferential direction due to pressure.

[0025] The uppermost part of the annular passage 91 communicates with the oil supply passage 92. The oil supply passage 92 is formed in an area above the axis O. As shown in FIG. 2, the oil supply passage 92 has a first part 33 formed inside the fixed scroll 31, a second part 62 formed in the bearing support part 61 and communicating with the first part 33, and a supply hole 93. The first part 33 penetrates the fixed scroll 31 in the axis O direction. One end of the first part 33 in the axis O direction is connected to the annular passage 91. The second part 62 extends in the axis O direction, and then changes direction and extends toward the guide recess 52 formed in the orbiting scroll 32. A supply hole 93 is formed in the downstream end of the second part 62. The supply hole 93 is capable of facing (communicating with) the guide recess 52 as the orbiting scroll 32 orbits.

[0026] Here, the orbiting radius ρ of the orbiting scroll 32 is determined by the above-mentioned rotation prevention mechanism 50. Specifically, the orbiting radius ρ is a value obtained by subtracting the radius of the pin 51 from the radius of the guide recess 52 (i.e., the radius of the inner periphery of the ring 53). Furthermore, as shown in FIG. 4, the shortest distance from the outer periphery of the orbiting scroll 32 to the inner periphery of the ring 53 is A, and the diameter of the supply hole 93 is φ. In this case, the dimensions of each part are set so that ρ>A and ρ>φ. The relationship φ>A is also satisfied.

[0027] (Action and effect) Next, the operation of the scroll compressor 100 will be described. To operate the scroll compressor 100, first, power is supplied to the electric motor 2. This causes the rotating shaft 1 to rotate about the axis O. The orbiting scroll 32 orbits about the axis O in association with the rotation of the rotating shaft 1. The volume of the compression chamber changes over time in association with this orbiting, and the refrigerant is gradually compressed. The compressed refrigerant passes through the high-pressure chamber 45 and is then guided to the outside.

[0028] On the other hand, the lubricating oil is introduced from the oil reservoir 41 to the introduction passage 42. After being decompressed in the introduction passage 42 by the decompression mechanism 43, the lubricating oil flows into the annular passage 91. The lubricating oil that flows upward in the annular passage 91 due to pressure is introduced to the oil supply passage 92. The lubricating oil that passes through this oil supply passage 92 is supplied to different parts depending on the orbiting position of the orbiting scroll 32. As shown in FIG. 4, when the orbiting scroll 32 is located at the uppermost position, the supply hole 93 faces the inside of the guide recess 52. As a result, the lubricating oil is supplied to the guide recess 52. On the other hand, as shown in FIG. 7, when the orbiting scroll 32 slightly orbits from the above state, the supply hole 93 faces the back surface 32s of the second end plate 32a. As a result, the back surface 32s is lubricated. Furthermore, as shown in FIG. 8, when the orbiting scroll 32 further orbits from the state of FIG. 7, the supply hole 93 is exposed to the outer periphery side of the orbiting scroll 32. This allows the lubricating oil to be supplied to the sliding portions of the orbiting scroll 32 and the fixed scroll 31. In this manner, by satisfying the above-mentioned dimensional relationship, it is possible to supply the lubricating oil to three different portions according to the orbiting position of the orbiting scroll 32.

[0029] In this manner, according to the above-described configuration, lubricating oil can be supplied to the guide recess 52 of the rotation prevention mechanism 50 through the supply hole 93. Furthermore, depending on the orbital position of the orbiting scroll 32, lubricating oil can be supplied not only to the guide recess 52 but also to the end face (rear face 32s) of the orbiting scroll 32 and the sliding portion between the orbiting scroll 32 and the fixed scroll 31.

[0030] In the above scroll compressor 100, when the orbital radius of the orbiting scroll 32, which is the radius of the guide recess 52 minus the radius of the pin 51, is ρ, the shortest distance from the outer peripheral surface of the orbiting scroll 32 to the inner peripheral surface of the guide recess 52 (i.e., the inner peripheral surface of the ring 53) is A, and the diameter of the supply hole 93 is φ, the relations ρ>A and ρ>φ are satisfied.

[0031] According to this configuration, by satisfying ρ>A and ρ>φ, the relative position of the supply hole 93 with respect to the orbiting scroll 32 changes depending on the orbiting position of the orbiting scroll 32. This makes it possible to more stably supply lubricating oil to the guide recess 52, the end face (rear face 32s) of the orbiting scroll 32, and the sliding parts between the orbiting scroll 32 and the fixed scroll 31.

[0032] In the above scroll compressor 100, when the shortest distance from the outer peripheral surface of the orbiting scroll 32 to the inner peripheral surface of the guide recess 52 (i.e., the inner peripheral surface of the ring 53) is A and the diameter of the supply hole 93 is φ, φ>A is satisfied.

[0033] According to this configuration, by satisfying φ>A, the supply hole 93 is not blocked by the orbiting scroll 32 while the orbiting scroll 32 is orbiting. This makes it possible to continuously supply the lubricating oil stably at all times.

[0034] The above describes the embodiment of the present disclosure. Various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure. For example, in the above embodiment, an example in which lubricating oil is supplied to one guide recess 52 through the oil supply passage 92 has been described. However, it is also possible to adopt a configuration in which the oil supply passage 92 communicates with multiple guide recesses 52.

[0035] <Additional Notes> The scroll compressor 100 described in each embodiment can be understood, for example, as follows.

[0036] (1) A scroll compressor 100 according to a first embodiment includes an electric motor 2, a rotating shaft 1 that is driven by the electric motor 2 to rotate about an axis O extending in a horizontal direction, a bearing portion (upper bearing 6) that supports the rotating shaft 1, an orbiting scroll 32 that orbits about the axis O as the rotating shaft 1 rotates, a fixed scroll 31 that faces the orbiting scroll 32 from one side in the direction of the axis O to form a compression chamber, a rotation prevention mechanism 50 provided on the orbiting scroll 32, and a lubricant for the rotation prevention mechanism 50. The rotation prevention mechanism 50 has a circular guide recess 52 formed on the back surface 32s of the rotating scroll 32 facing the other side in the direction of the axis O, and a pin 51 fixed to the bearing portion and inserted into the guide recess 52, and guides the rotation of the rotating scroll 32 by abutting against the inner surface of the guide recess 52, and the oil supply passage 92 is formed in the bearing portion and has a supply hole 93 facing the guide recess 52 as the rotating scroll 32 rotates.

[0037] According to the above-described configuration, lubricating oil can be supplied to the guide recess 52 through the supply hole 93. Furthermore, depending on the orbital position of the orbiting scroll 32, lubricating oil can be supplied not only to the guide recess 52 but also to the end face of the orbiting scroll 32 and the sliding portion between the orbiting scroll 32 and the fixed scroll 31.

[0038] (2) In the scroll compressor 100 of the second aspect, when the orbiting radius of the orbiting scroll 32, which is the radius of the guide recess 52 minus the radius of the pin 51, is ρ, the shortest distance from the outer peripheral surface of the orbiting scroll 32 to the inner peripheral surface of the guide recess 52 is A, and the diameter of the supply hole 93 is φ, the relations ρ>A and ρ>φ are satisfied.

[0039] According to the above configuration, by satisfying ρ>A and ρ>φ, the relative position of the supply hole with respect to the orbiting scroll 32 changes according to the orbiting position of the orbiting scroll 32. This makes it possible to more stably supply lubricating oil to the guide recess 52, the end face of the orbiting scroll 32, and the sliding portion between the orbiting scroll 32 and the fixed scroll 31.

[0040] (3) In the scroll compressor 100 according to the third aspect, when the shortest distance from the outer circumferential surface of the orbiting scroll 32 to the inner circumferential surface of the guide recess 52 is A and the diameter of the supply hole 93 is φ, φ>A is satisfied.

[0041] According to the above configuration, by satisfying φ>A, the supply hole 93 is not blocked by the orbiting scroll 32 while the orbiting scroll 32 is orbiting. This makes it possible to continuously supply the lubricating oil stably at all times. [Explanation of symbols]

[0042] 100 Scroll Compressor 1 Rotation axis 2 electric motor 3 Compressor body 4. Housing 4a First Housing 4b Second housing 4s Housing end face 5 Cover 6 Upper bearing 7 Lower Bearing 8 Drive bush 9 Seal Part 9´ Seal body 9a Outer seal part 9b Inner seal part 9a´,9b´ Convex part 10 Rotating shaft body 11 Small diameter section 12 Large diameter section 13 Eccentric shaft part 21 Rotor 22 Stator 31 Fixed Scroll 31a First end plate 31b First spiral plate 31s main surface 32 Swivel Scroll 32a Second end plate 32b Second spiral plate 32c boss part 32s back 33 First part 41 Oil Reservoir 42 Inlet Channel 43 Pressure reducing mechanism 44 Oil separator 45 Hyperbaric Chamber 46 Bulkhead 50 Anti-rotation mechanism 51 pin 52 Guide recess 53 Ring 60 Bearing body 61 Bearing support part 62 Second part 91 Annular flow path 92 Oil supply passage 93 Supply hole A Eccentric shaft H opening O axis

Claims

1. An electric motor; a rotating shaft that is driven by the electric motor to rotate about an axis extending in a horizontal direction; A bearing portion that supports the rotating shaft; an orbiting scroll that orbits about the axis as the rotation shaft rotates; a fixed scroll that faces the orbiting scroll from one side in the axial direction to form a compression chamber; A rotation prevention mechanism provided on the orbiting scroll; an oil supply passage capable of supplying lubricating oil to the rotation prevention mechanism; Equipped with The rotation prevention mechanism includes: A circular guide recess is formed on a back surface of the orbiting scroll facing the other side in the axial direction; a pin that is fixed to the bearing portion and is inserted into the guide recess so as to abut against an inner circumferential surface of the guide recess to guide the orbiting of the orbiting scroll; having the oil supply passage is formed in the bearing portion and has a supply hole opening to one side in the axial direction, The supply hole is in one of three states: facing the guide recess, facing the back surface, or exposed on the outer circumferential side of the orbiting scroll, depending on the orbital position of the orbiting scroll.

2. 2. The scroll compressor according to claim 1, wherein, when a radius of rotation of the orbiting scroll, which is a value obtained by subtracting a radius of the pin from a radius of the guide recess, is ρ, a shortest distance from an outer peripheral surface of the orbiting scroll to an inner peripheral surface of the guide recess is A, and a diameter of the supply hole is φ, the relationships ρ > A and ρ > φ are satisfied.

3. 3. The scroll compressor according to claim 1, wherein A is a shortest distance from an outer circumferential surface of the orbiting scroll to an inner circumferential surface of the guide recess, and φ is a diameter of the supply hole, and φ>A is satisfied.

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