JP6029517B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor mounted mainly in a refrigerator, an air conditioner, a water heater, or the like.

  A conventional scroll compressor includes an Oldham ring for preventing the rotation of the orbiting scroll. The Oldham ring is generally formed in an annular shape, and has key portions on the upper and lower surfaces. The key portions are fitted to the key groove portions of the orbiting scroll and the key groove portions of the frame to prevent rotation. The Oldham ring configured and arranged in this manner has a problem that the key portion is inclined due to a load acting on the key portion during operation, and the key portion and the key groove portion wear against each other.

  As a technique for solving this problem, there is a technique in which an oil holding portion that holds lubricating oil is provided on a sliding surface of a key portion with a key groove (see, for example, Patent Document 1).

  Also, among the sliding surfaces of the key portion with the key groove, a curved sliding surface is provided at the corner including the sliding surface on the outer diameter side of the Oldham ring, and lubricating oil is provided between the key portion and the key groove. There is a technique for preventing wear due to scraping (see, for example, Patent Document 2).

Japanese Patent Laid-Open No. 2002-349457 (page 4, FIG. 3) Japanese Unexamined Patent Publication No. 2004-19488 (page 7, FIG. 3)

  In Patent Documents 1 and 2 above, although a certain effect can be expected in terms of improvement in wear due to the key portion of the Oldham ring hitting the key groove portion, further improvement is required.

  The present invention was made to solve the above-described problems, and an object of the present invention is to obtain a highly reliable scroll compressor by suppressing wear caused by the key portion of the Oldham ring hitting the key groove. And

A scroll compressor according to the present invention drives a compression mechanism portion via a crankshaft, and a compression mechanism portion that compresses refrigerant in a compression chamber formed by meshing a swing scroll and a fixed scroll in a sealed container. Provided between the drive mechanism section, the compression mechanism section and the drive mechanism section, and a frame for fixing the compression mechanism section to the sealed container, and an Oldham ring for preventing the rotation of the orbiting scroll. A scroll compressor in which a formed key portion reciprocally slides in a rocking scroll and a key groove formed in a frame, the key portion on an annular ring protruding in an axial direction from an annular portion of an Oldham ring A projecting portion and a radially projecting portion projecting radially outward from the projecting portion on the ring, and the radially projecting portion leaves a load receiving portion that slides with the keyway when the crankshaft rotates. Has a configuration in which notched portion is formed, the key unit is one that is configured so as to satisfy the following.
L2 <L1 <L0 and L3 <L4
here,
L0: Total radial length of the annular projecting portion and the load receiving portion L1: Width of the annular portion of the Oldham ring L2: Radial length of the notched portion of the radial projecting portion L3: Load receiving portion Width in the circumferential direction on the outer diameter side L4: Width in the circumferential direction on the inner diameter side of the swing side key part

  ADVANTAGE OF THE INVENTION According to this invention, the wear by the key part of Oldham ring hitting a key groove can be suppressed, and a highly reliable scroll compressor can be obtained.

It is a schematic sectional drawing of the hermetic scroll compressor 100 in Embodiment 1 of this invention. 1 is an overall view of an Oldham ring 20 of a scroll compressor 100 according to Embodiment 1 of the present invention. FIG. 3 is a partially enlarged plan view of a swing side key portion 22 of the Oldham ring 20 of FIG. 2. It is a deformation | transformation schematic diagram of the Oldham ring 20 of the scroll compressor 100 in Embodiment 1 of this invention. It is a deformation | transformation schematic diagram of the key part 220 in a prior art example. It is a deformation | transformation schematic diagram of the rocking | swiveling side key part 22 of the scroll compressor 100 in Embodiment 1 of this invention. It is a schematic sectional drawing of the scroll compressor 101 in Embodiment 2 of this invention.

Embodiment 1 FIG.
The first embodiment will be described below with reference to FIGS.

FIG. 1 is a schematic cross-sectional view of a hermetic scroll compressor 100 according to Embodiment 1 of the present invention.
The scroll compressor 100 has a function of sucking a fluid such as a refrigerant, compressing it, and discharging it in a high temperature / high pressure state. The scroll compressor 100 includes a compression mechanism section 35, a drive mechanism section 36 that drives the compression mechanism section 35 via the crankshaft 4, and other components, and these are the inside of the shell 8 that forms the outer shell. It has the structure accommodated in. As shown in FIG. 1, the compression mechanism 35 is disposed on the upper side and the drive mechanism 36 is disposed on the lower side in the shell 8. The lower part of the shell 8 is an oil sump 12 for storing lubricating oil.

  Furthermore, the frame 3 and the sub-frame 16 are arranged on the shell 8 so as to face each other with the compression mechanism portion 35 interposed therebetween. The frame 3 is disposed on the upper side of the compression mechanism unit 35 and is positioned between the compression mechanism unit 35 and the drive mechanism unit 36, and the subframe 16 is positioned on the lower side of the compression mechanism unit 35. The frame 3 and the sub frame 16 are fixed to the inner peripheral surface of the shell 8 by shrink fitting, welding, or the like. Through holes 4b and 16b are provided in the central portions of the frame 3 and the sub frame 16, and the crankshaft 4 is rotatably supported by the main bearing 3a and the sub bearing 16a provided in the through holes 4b and 16b. .

  The shell 8 is provided with a suction pipe 5 for sucking fluid and a discharge pipe 13 for discharging fluid.

  The compression mechanism 35 has a function of compressing the fluid sucked from the suction pipe 5 and discharging it to the high-pressure space 14 formed above the shell 8. The compression mechanism unit 35 includes a fixed scroll 1 and a swing scroll 2. The fixed scroll 1 is disposed on the upper side and is fixed to the shell 8 via the frame 3, and the orbiting scroll 2 is disposed on the lower side and is supported on the crankshaft 4 so as to be freely swingable.

  The fixed scroll 1 includes a first base plate 1c and a first spiral body 1b which is a spiral projection standing on one surface of the first base plate 1c. The orbiting scroll 2 includes a second base plate 2c and a second spiral body 2b that is a spiral projection standing on one surface of the second base plate 2c. The first spiral body 1b and the second spiral body 2b are created following an involute curve. The fixed scroll 1 and the orbiting scroll 2 are mounted in the shell 8 in a state where the first spiral body 1b and the second spiral body 2b are engaged with each other. A compression chamber 9 is formed between the first spiral body 1b and the second spiral body 2b. The compression chamber 9 decreases in volume as it goes inward in the radial direction as the crankshaft 4 rotates.

  A discharge port 1 a that discharges a compressed and high-pressure fluid is formed at the center of the fixed scroll 1. A leaf spring valve 11 is provided at the outlet opening of the discharge port 1a so as to cover the outlet opening and prevent backflow of fluid. A valve retainer 10 that restricts the lift amount of the valve 11 is fixed to one end side of the valve 11. That is, when the fluid is compressed to a predetermined pressure in the compression chamber 9, the valve 11 is lifted against the elastic force and the discharge port 1a is opened. The compressed fluid is discharged from the opened discharge port 1 a into the high-pressure space 14, and discharged to the outside of the scroll compressor 100 through the discharge pipe 13.

  The orbiting scroll 2 performs an eccentric turning motion without rotating with respect to the fixed scroll 1. A hollow cylindrical concave bearing 2d that receives a driving force is formed at a substantially central portion of a surface (hereinafter referred to as a thrust surface) opposite to the surface on which the second spiral body 2b is formed of the orbiting scroll 2. Yes. An eccentric pin portion 4a (described later) provided at the upper end of the crankshaft 4 is fitted (engaged) with the concave bearing 2d.

  The drive mechanism unit 36 includes a stator 7 and a rotor 6. The stator 7 has a function of rotating the rotor 6 when energized. The stator 7 is formed in a substantially cylindrical shape, and its outer peripheral surface is fixedly supported on the shell 8 by shrink fitting or the like. The rotor 6 is fixed to the outer periphery of the crankshaft 4, has a permanent magnet inside, and is rotatably held inside the stator 7 with a slight gap from the stator 7. The rotor 6 is rotationally driven when the stator 7 is energized to rotate the crankshaft 4. That is, when the rotor 6 rotates, rotational power is transmitted to the compression mechanism portion 35 via the crankshaft 4.

  The crankshaft 4 is rotatably supported by a main bearing 3 a provided on the frame 3 on the upper side and rotatably supported by a sub-bearing 16 a provided on the subframe 16 on the lower side. The crankshaft 4 has an eccentric pin portion 4a at the upper end, and the eccentric pin portion 4a is fitted with the concave bearing 2d of the orbiting scroll 2, and the orbiting scroll 2 is eccentrically swung by the rotation of the crankshaft 4. It is like that.

  In the shell 8, an Oldham ring 20 is arranged between the swing scroll 2 and the frame 3 for preventing the swing scroll 2 from rotating during the eccentric orbiting motion of the swing scroll 2.

  In the scroll compressor 100 configured as described above, when a power supply terminal (not shown) provided in the shell 8 is energized, torque is generated in the stator 7 and the rotor 6 and the crankshaft 4 rotates. Then, the rotation of the crankshaft 4 causes the orbiting scroll 2 to perform an eccentric orbiting movement, and the compression chamber 9 moves while reducing the volume toward the center. Thereby, the refrigerant in the compression chamber 9 is compressed.

  Next, the Oldham ring 20 which is a characteristic part in the scroll compressor 100 of the first embodiment will be described.

2A and 2B are overall views of the Oldham ring 20 of the scroll compressor 100 according to the first embodiment of the present invention, where FIG. 2A is a plan view and FIG. 2B is a cross-sectional view taken along line AA of FIG. In FIG. 2, thin arrows indicate the rotation direction of the crankshaft 4.
The Oldham ring 20 has an annular ring portion 21 and has a configuration in which a pair of key portions 22 and 23 project from both surfaces thereof. The pair of key portions 22 are arranged on a substantially straight line on the upper surface side of the annular portion 21, and the pair of key portions 23 are arranged on a substantially straight line on the lower surface side of the annular portion 21.

  The pair of key portions 22 on the swing scroll 2 side and the pair of key portions 23 on the frame 3 side are formed to have a phase difference of approximately 90 °. Hereinafter, the key portion 22 on the swing scroll 2 side is referred to as the swing side key portion 22, and the key portion 23 on the frame 3 side is referred to as the frame side key portion 23. In the case where the swing side key portion 22 and the frame side key portion 23 are not particularly distinguished, they may be simply referred to as a key portion.

  The arrangement of the Oldham ring 20 will be described in more detail. A pair of key grooves 30A are formed in a substantially straight line on the thrust surface of the second base plate 2c of the orbiting scroll 2, and a pair of orbiting-side key portions 22 of the Oldham ring 20 are formed in the pair of key grooves 30A. Are engaged so as to be slidable back and forth in the radial direction. On the other hand, the frame 3 is also formed with a pair of key grooves 30B substantially in a straight line, and the pair of key-side key portions 23 of the Oldham ring 20 can be reciprocally slidable in the radial direction in the pair of key grooves 30B. Is engaged. Thus, when the key portions 22 and 23 of the Oldham ring 20 are engaged with the key grooves 30A and 30B, the rotation of the orbiting scroll 2 is prevented and the refrigerant can be compressed.

FIG. 3 is a partially enlarged plan view of the swing side key portion 22 of the Oldham ring 20 of FIG. In FIG. 3, thin arrows indicate the rotation direction of the crankshaft 4.
The swing-side key portion 22 includes an annular upper protrusion 22a protruding from the annular portion 21 toward the swing scroll 2, and a radial protrusion 22b protruding radially outward from the annular protrusion 22a. have. The radial protrusion 22b has a configuration in which a notch 22d is formed leaving a load receiving portion 22c that slides with the key groove 30A when the crankshaft 4 rotates. The load receiving portion 22c is positioned on the rotational direction side of the crankshaft 4 in the radial protruding portion 22b, and the end surfaces on the rotating direction side of the load receiving portion 22c and the annular protruding portion 22a are the key grooves 30A. And a sliding surface that slides.

The swing side key portion 22 is configured to satisfy L2 <L1 <L0 and L3 <L4.
here,
L0: Total radial length of the annular upper protruding portion 22a and the load receiving portion 22c L1: Width of the annular portion 21 of the Oldham ring 20 L2: The radial direction of the notched portion 22d of the radial protruding portion 22b Length L3: Width in the circumferential direction on the outer diameter side of the load receiving portion 22c L4: Width in the circumferential direction on the inner diameter side (lower side in FIG. 3) of the swinging side key portion 22 (circumferential direction of the annular upper protrusion 22a) Same as width)

  Here, the swing-side key portion 22 has been described, but the frame-side key portion 23 has the same configuration, and the frame-side key portion 23 includes an annular upper protrusion 23a and a radial protrusion 23b. The radial protrusion 23b has a load receiving portion 23c and a notch 23d. In the frame side key portion 23, the load receiving portion 23c is as shown in FIG. 2 because the load applied during rotation of the swing side key portion 22 and the crankshaft 4 is reversed as will be described in detail below. The radial protrusion 23b is located on the opposite side of the rotation direction of the crankshaft 4.

  Next, deformation of the Oldham ring 20 due to a load acting on the Oldham ring 20 when the scroll compressor 100 is driven will be described.

  4A and 4B are schematic diagrams of deformation of the Oldham ring 20 of the scroll compressor 100 according to Embodiment 1 of the present invention, where FIG. 4A shows before deformation and FIG. 4B shows after deformation. In FIG. 4, thin arrows indicate the rotation direction of the crankshaft 4. In FIG. 4, a solid white arrow is a load acting on the swing side key portion 22 of the Oldham ring 20, and a dotted white arrow is a load acting on the frame side key portion 23. In addition, illustration of radial direction protrusion part 22b, 23b is abbreviate | omitted in FIG.

  The swing scroll 2 generates a load that tends to rotate due to a reaction force that compresses the refrigerant. The swing-side key portion 22 and the frame-side key portion 23 provided on both surfaces of the Oldham ring 20 support the load to be rotated. As described above, the Oldham ring 20 supports the load to be rotated by the swing side key portion 22 and the frame side key portion 23, and thus the annular portion 21 is deformed into an elliptical shape as shown in FIG. 4B.

  FIGS. 5A and 5B are deformation schematic diagrams of the key unit 220 in the conventional example, in which FIG. 5A shows before deformation and FIG. 5B shows after deformation. FIG. 6 is a schematic diagram of deformation of the swing side key portion 22 of the scroll compressor 100 according to Embodiment 1 of the present invention, where (a) shows before deformation and (b) shows after deformation. 5 and 6, thin arrows indicate the rotation direction of the crankshaft 4.

  In the conventional example shown in FIG. 5, when a load is applied to the key portion 220, the key portion 220 and the annular portion 210 of the Oldham ring 200 are deformed, and the key portion 220 is changed to the key portion as shown in FIG. The groove 300 is inclined with respect to the side surface portion 300a and hits one side. As a result, the key portion 220 is easily worn. On the other hand, in the first embodiment as well, the annular portion 21 is deformed as shown in FIG.

  However, in the first embodiment, the radial protrusion 22b of the swinging key part 22 has a notch 22d, and the rigidity of the outer diameter side of the swinging key part 22 is smaller than that of the inner diameter side. It is configured. For this reason, as shown in FIG.6 (b), the load receiving part 22c deform | transforms following the side part 30a of the keyway 30A, and it becomes difficult to carry out a piece contact. That is, the swing side key portion 22 comes into surface contact with the side surface portion 30a of the key groove 30A, and the contact area increases. As the area receiving the load increases in this way, the surface pressure decreases, and wear of the swinging key part 22 can be prevented. For this reason, the highly reliable scroll compressor 100 can be obtained.

  Further, the scraping-off effect described above suppresses scraping of the lubricating oil between the swing side key portion 22 and the side surface portion 30a of the key groove 30A, and the side surface portion 30a of the swing side key portion 22 and the key groove 30A. It is considered that an oil film is likely to be generated between the two.

  Here, the swing-side key portion 22 has been described, but the same function and effect can be obtained also in the frame-side key portion 23.

Next, the effect when an aluminum material is used for the Oldham ring 20 will be described.
Since the Oldham ring 20 repeats reciprocating motion in the radial direction, the radial center of gravity changes during one rotation, and it is difficult to achieve a perfect balance. Therefore, due to the unbalance amount accompanying the reciprocating motion of the Oldham ring 20, the vibration increases and the noise increases. Therefore, in order to reduce the unbalance amount, an aluminum material having a low density is often used as a metal in recent years.

  However, since the aluminum material has a small Young's modulus as a metal and has a low strength, the amount of deformation when a load is applied to the key portion is larger than that of other iron materials. Therefore, the angle at which the key portion tilts increases, and the area per side with the key groove becomes smaller and wear tends to increase. However, if this invention is used, since the surface pressure of the sliding surface of the key parts 22 and 23 and the key grooves 30A and 30B can be reduced, it is considered that the effect is greater.

Next, the effect when R32 is used as the refrigerant will be described.
In recent years, switching from R410A refrigerant to R32 refrigerant having a low global warming potential (GWP) has been studied from the viewpoint of preventing global warming, particularly in the air conditioner field. When R32 is used, the pressure increases as compared with R410A, so that the load acting on the key portions 22 and 23 of the Oldham ring 20 increases. However, if the present invention is used, the surface pressure at the key portions 22 and 23 can be lowered, and the effect is particularly great.

Embodiment 2. FIG.
In the first embodiment, the Oldham ring 20 is arranged with the orbiting scroll 2 and the frame 3, but in the second embodiment, the Oldham ring 20 is arranged between the orbiting scroll 2 and the fixed scroll 1. This is the configuration.

  FIG. 7 is a schematic cross-sectional view of scroll compressor 101 according to Embodiment 2 of the present invention. FIG. 7 is the same as the first embodiment except for the arrangement positions of the scroll compressor 100 and the Oldham ring 20 of the first embodiment shown in FIG.

  In the scroll compressor 101 of the second embodiment, a pair of key grooves 30B are provided on the upper surface side (the second spiral body 2b forming surface side) of the second base plate 2c of the orbiting scroll 2, and the first scroll 1 of the fixed scroll 1 is provided. A pair of key grooves 30C are provided on the lower surface side (the first spiral body 1b forming surface side) of the base plate 1c. The Oldham ring 20 is disposed between the pair of key grooves 30B and the pair of key grooves 30C.

  In the scroll compressors 100 and 101, the lubricant stored in the bottom of the shell 8 is sucked up by an oil pump (not shown) driven by the rotation of the crankshaft 4, and then swings through the crankshaft 4. It is supplied to the lower surface (thrust surface) of the scroll 2. For this reason, in the scroll compressor 100 of Embodiment 1, the Oldham ring 20 is immersed in lubricating oil. However, in the scroll compressor 101 of the second embodiment, the Oldham ring 20 is disposed on the upper surface of the orbiting scroll 2, and therefore, the lubricating oil is supplied to the Oldham ring 20 only by the winding with the refrigerant. That is, the key portions 22 and 23 are required to be reliable in a state where the amount of lubricating oil is smaller. Here, if the present invention is used, the surface pressure of the key portions 22 and 23 can be lowered, and therefore, even when the Oldham ring 20 is arranged on the upper surface of the orbiting scroll 2, sufficient reliability can be ensured.

  DESCRIPTION OF SYMBOLS 1 Fixed scroll, 1a Discharge port, 1b 1st spiral body, 1c 1st base plate, 2 Swing scroll, 2b 2nd spiral body, 2c 2nd base plate, 2d Concave bearing, 3 Frame, 3a Main bearing, 4 Crank Shaft, 4a Eccentric pin part, 4b Through hole, 5 Suction pipe, 6 Rotor, 7 Stator, 8 Shell, 9 Compression chamber, 10 Valve presser, 11 Valve, 12 Oil reservoir, 13 Discharge pipe, 14 High pressure space, 16 Subframe , 16a Sub-bearing, 16b Through-hole, 20 Oldham ring, 21 Annular part, 22 Key part (oscillating side key part), 22a Annular projection part, 22b Radial projecting part, 22c Load receiving part, 22d Notch Part, 23 key part (frame side key part), 23a annular projecting part, 23b radial projecting part, 23c load receiving part, 23d notch part, 30A key groove, 0B key groove, 30C key groove, 30a side surface part, 35 compression mechanism part, 36 drive mechanism part, 100 scroll compressor, 101 scroll compressor, 200 Oldham ring, 210 ring part, 220 key part, 300 key groove, 300a Side part.

Claims (4)

A compression mechanism that compresses the refrigerant in a compression chamber formed by meshing a swing scroll and a fixed scroll in an airtight container, a drive mechanism that drives the compression mechanism via a crankshaft, and the compression mechanism Provided on the both sides of the Oldham ring, provided with a frame for fixing the compression mechanism portion to the sealed container and an Oldham ring for preventing rotation of the orbiting scroll. A scroll compressor that reciprocally slides in a key groove formed in the swing scroll and the frame, respectively,
The key portion includes an annular upper projecting portion projecting in an axial direction from an annular portion of the Oldham ring, and a radial projecting portion projecting radially outward from the annular upper projecting portion, The radial protrusion has a configuration in which a notch is formed leaving a load receiving portion that slides with the keyway when the crankshaft rotates.
A scroll compressor characterized in that the key portion is configured to satisfy the following.
L2 <L1 <L0 and L3 <L4
here,
L0: Total radial length of the annular projecting portion and the load receiving portion L1: Width of the annular portion of the Oldham ring L2: Radial length of the notched portion of the radial projecting portion L3: Load receiving portion Width in the circumferential direction on the outer diameter side L4: Width in the circumferential direction on the inner diameter side of the swing side key part A compression mechanism that compresses the refrigerant in a compression chamber formed by meshing a swing scroll and a fixed scroll in an airtight container, a drive mechanism that drives the compression mechanism via a crankshaft, and the compression mechanism Provided on the both sides of the Oldham ring, provided with a frame for fixing the compression mechanism portion to the sealed container and an Oldham ring for preventing rotation of the orbiting scroll. A scroll compressor that reciprocally slides in a key groove formed in each of the swing scroll and the fixed scroll,
The key portion includes an annular upper projecting portion projecting in an axial direction from an annular portion of the Oldham ring, and a radial projecting portion projecting radially outward from the annular upper projecting portion, The radial protrusion has a configuration in which a notch is formed leaving a load receiving portion that slides with the keyway when the crankshaft rotates.
A scroll compressor characterized in that the key portion is configured to satisfy the following.
L2 <L1 <L0 and L3 <L4
here,
L0: Total radial length of the annular projecting portion and the load receiving portion L1: Width of the annular portion of the Oldham ring L2: Radial length of the notched portion of the radial projecting portion L3: Load receiving portion Width in the circumferential direction on the outer diameter side L4: Width in the circumferential direction on the inner diameter side of the swing side key part 3. The scroll compressor according to claim 1, wherein the Oldham ring is made of an aluminum material. The scroll compressor according to any one of claims 1 to 3, wherein the refrigerant is R32.

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