JP6328330B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor used for an air conditioner, a refrigerator, or the like.

Conventionally, this type of scroll compressor includes a hermetic container, a fixed scroll fixed in the hermetic container, an orbiting scroll having a center of rotation eccentric with respect to the center of the fixed scroll, and a stator and a rotor constituting an electric motor. A spindle that is driven to rotate by an electric motor, a slider that supports the orbiting scroll to revolve the orbiting scroll, and a slider mounting shaft that is installed above the main axis so that the slider is eccentric with respect to the main axis. An eccentric shaft part, a suction pipe for introducing refrigerant gas into the sealed container from the outside, a discharge pipe for discharging refrigerant gas compressed by the compression part to the outside, an orbiting scroll, a thrust plate, Oldham A frame that supports the ring and main shaft and is fixed to the fixed scroll with bolts, etc., and the main shaft is rotatably supported at the bottom of the compression section And a sub-frame, and a, and the oil pump displacement type which sucks up the slider through the oil supply passage in the bottom oil accumulated spindle in the closed container. A slit for flowing oil in the opposite direction to the bearing load and in the axial direction is provided on the outer periphery of the slider. As a result, the oil sucked up to the slider by the oil pump flows from the top to the bottom in the axial direction through the slit on the slider outer periphery, so that the oil is supplied to the sliding portion between the slider outer periphery and the rocking bearing. It has become.

JP 2012-189003 A

As described above, the outer periphery of the slider in the conventional scroll compressor is provided with a slit having a uniform cross-sectional shape in the opposite direction to the bearing load and in the axial direction. Under the condition that the oil concentration is lowered by dilution, the sliding friction of the bearing is likely to increase, so that the lubricity deteriorates and the current value may increase. In such a case, since the viscosity of the oil is low, the flow rate of the oil flowing in the slit is increased, and there is a problem that it is difficult to supply the oil to the sliding portion of the rocking bearing.

  The present invention has been made to solve the above-described problems, and supplies a sufficient amount of oil to a rocking bearing even under conditions where the oil concentration in the sealed container is low. The purpose is to obtain a scroll compressor that can be used.

A scroll compressor according to the present invention includes a sealed container, a fixed scroll fixedly arranged in the sealed container, an orbiting scroll that swings and swings with respect to the fixed scroll to form a compression chamber between the fixed scroll, A cylindrical oscillating bearing provided upright on the surface opposite to the surface facing the fixed scroll in the oscillating scroll, and a slotted hole inserted into the cylindrical hole of the oscillating bearing and supported slidably. A cylindrical slider having a cylindrical bearing hole, a rotary drive shaft having an oil hole that is fixed to the rotor of an electric motor disposed in a sealed container and penetrates in the axial direction, and is connected to one end surface of the rotary drive shaft An oil pump that pumps the lubricating oil in the sealed container into the oil hole, and is formed at a position deviated from the axis of the rotary drive shaft on the other end surface of the rotary drive shaft and is inserted into the bearing hole of the slider and slides. Freely An eccentric shaft portion that is held and has an oil hole from the rotation drive shaft, and a cutout portion formed by cutting out a part of the outer peripheral surface of the slider along the cylinder center direction. A first cutout portion formed on one end side, and a second cutout portion formed on the other end side with a larger cutaway cross-sectional area as viewed in the axial direction than the first cutout portion The step part is provided between the 1st notch part and the 2nd notch part.

In the scroll compressor according to the present invention, the notch portion of the slider includes a first notch portion on one end side and a second notch portion on the other end side having a larger notch cross-sectional area than the first notch portion. Since the step portion is provided between the first notch portion and the second notch portion, the flow path area when oil flows from the end surface on the other end side of the slider to the one end side through the notch portion. Is wider at the second cutout portion on the other end side than the step portion, and narrower at the first cutout portion on the one end side than the step portion. Accordingly, the amount of oil present in the second cutout portion on the other end side of the step portion is larger than that in the first cutout portion. Incidentally, since the viscosity of the oil is low under the condition where the oil concentration is low, the flow rate of the oil flowing through the notch of the slider is determined by the first notch having a small notch cross-sectional area (= channel area). . Accordingly, the second cutout portion having a large flow path area can make the oil flow rate slower than the first cutout portion having a small flow path area. As a result, the second notch portion having a low flow velocity can easily draw oil into the sliding portion formed of a rocking bearing or the like. In addition, since the amount of oil present in the second notch increases, the amount of oil supplied to the sliding portion can be increased.

It is a longitudinal cross-sectional view of the scroll compressor in Embodiment 1 of this invention. It is a figure which shows the slider and rocking | fluctuation bearing in Embodiment 1 of this invention, Comprising: (a) is a top view, (b) is a sectional side view. It is a longitudinal cross-sectional view which shows the eccentric shaft part and slider in Embodiment 1 of this invention. It is an external view of the slider of the scroll compressor in Embodiment 2 of this invention. It is an external view of the slider of the scroll compressor in Embodiment 3 of this invention. It is an external view of the slider of the scroll compressor in Embodiment 4 of this invention. It is a figure which shows the slider of the scroll compressor in Embodiment 5 of this invention, Comprising: (a) is an external view, (b) is a sectional side view.

Embodiment 1 FIG.
1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1 of the present invention.
In the figure, a scroll compressor 100 sucks a refrigerant circulating in the refrigeration cycle, compresses it, and discharges it as a high temperature and high pressure state. The scroll compressor 100 includes a compression unit including a fixed scroll 9 and a swing scroll 10 and a drive unit including an electric rotary machine 7 and the like. These compression part and drive part are accommodated in the hermetic container 1. The sealed container 1 is a container in which an upper container 1c and a lower container 1b are connected in a sealed manner to an upper part and a lower part of an intermediate container 1a. The lower container 1b has an oil sump 23 for storing lubricating oil. A suction pipe 24 for sucking refrigerant gas is connected to the intermediate container 1a. A discharge pipe 25 for discharging refrigerant gas is connected to the upper container 1c.

  The compression unit supports the fixed scroll 9 fixedly arranged in the hermetic container 1, the swing scroll 10 that swings and swings with respect to the fixed scroll 9 to form the compression chamber 26 with the fixed scroll 9, and these. It consists of a frame 11 and the like. The swing scroll 10 is disposed on the lower side, and the fixed scroll 9 is disposed on the upper side. In addition, a thrust plate 14 that supports the swing scroll 10 is provided between the swing scroll 10 and the frame 11. That is, the thrust bearing is configured by the rocking scroll 10 and the thrust plate 14 being in close contact with each other via the lubricating oil.

  The fixed scroll 9 is formed with a wrap portion 9a which is a spiral protrusion standing on one surface. Further, the oscillating scroll 10 is also formed with a wrap portion 10a which is a spiral protrusion which is erected on one surface and has substantially the same shape as the wrap portion 9a. The orbiting scroll 10 and the fixed scroll 9 are provided in the sealed container 1 in a state where the wrap portion 10a and the wrap portion 9a are combined with each other. In a state where the swing scroll 10 and the fixed scroll 9 are combined, the winding directions of the wrap portion 9a and the wrap portion 10a are opposite to each other. And the compression chamber 26 from which a volume changes relatively is formed between the lap | wrap part 10a and the lap | wrap part 9a. The fixed scroll 9 and the orbiting scroll 10 are provided with seals 27 and 28 at the front end surfaces of the wrap portion 9a and the wrap portion 10a in order to reduce refrigerant leakage from the front end surfaces of the wrap portion 9a and the wrap portion 10a. Yes.

  The fixed scroll 9 is fixed to the frame 11 with a bolt or the like (not shown). A discharge port 9 b that discharges the compressed refrigerant gas to a high pressure is formed at the center of the fixed scroll 9. Then, the compressed refrigerant gas having a high pressure is discharged into a discharge space 33 provided in the upper part of the fixed scroll 9. The orbiting scroll 10 performs a revolving orbiting motion (oscillating motion) without rotating about the fixed scroll 9 by an Oldham ring 15 for preventing the rotating motion. A hollow cylindrical rocking bearing 13 is formed at a substantially central portion of a lower surface (= thrust surface) 10b opposite to the surface on which the wrap portion 10a is formed of the rocking scroll 10. The oscillating bearing 13 is rotatably provided with a cylindrical slider 16 which is inserted into the cylindrical hole 13a and slidably supported and has a long bearing hole 16j. An eccentric shaft portion 4 a formed on the other end surface 4 e of the main shaft 4 is inserted into the bearing hole 16 j (FIG. 3) of the slider 16. The eccentric shaft portion 4a is formed at a position offset from the axis C of the main shaft 4 on the other end surface 4e of the main shaft 4, is inserted into the bearing hole 16j of the slider 16 and is slidably supported, and the main shaft 4 It has an oil 4c hole connected from. The inner peripheral part of the rocking bearing 13 and the outer peripheral surface 16b of the slider 16 are in close contact with each other through the lubricating oil, thereby constituting the rocking bearing part.

FIG. 2 shows a plan view and a side sectional view of the slider 16 and the rocking bearing 13. FIG. 3 shows a longitudinal sectional view of the eccentric shaft portion 4 a and the slider 16. A slider plate 16a is disposed between the inner peripheral surface of the bearing hole 16j of the slider 16 and the eccentric shaft portion 4a. On the outer circumferential surface of the eccentric shaft portion 4a, a crowning portion 4d that bulges outward in the radial direction and contacts the slider plate 16a is formed on the load surface facing the slider plate 16a. The crowning portion 4d has an arc shape in the longitudinal section.

A part of the outer peripheral surface 16b of the slider 16 is formed with a notch 16m for flowing oil in the opposite direction to the bearing load and in the axial direction. As a result, the oil sucked up to the slider 16 by the positive displacement oil pump 22 flows from the upper side to the lower side in the axial direction through the notch 16m, so that the outer peripheral surface 16b of the slider 16 and the rocking bearing 13 are formed. Oil is supplied to the sliding portion.
In particular, the step portion 16f of the slider 16 is formed at a position farther from the end surface 16c on the other end side of the slider 16 than the contact surface 34 between the slider plate 16a and the crowning portion 4d. That is, in this embodiment, the step portion 16f of the slider 16 is disposed at a position lower than the contact surface 34 between the slider plate 16a and the crowning portion 4d. 3, reference numeral 16g denotes a wall surface of the first cutout portion 16e, and 16h denotes a wall surface of the second cutout portion 16d.

  The drive unit described above includes a main shaft 4 that is a rotational drive shaft, a rotor 3 fixed to the main shaft 4, a stator 2, and the like. The rotor 3 is rotationally driven when the energization of the stator 2 starts to rotate the main shaft 4. That is, the stator 2 and the rotor 3 constitute an electric rotary machine (= electric motor) 7.

  The main shaft 4 has an oil hole 4c that is fixed to the rotor 3 of the electric rotary machine 7 disposed in the hermetic container 1 and penetrates in the direction of the axis C, and rotates as the rotor 3 rotates. The swing scroll 10 is turned. The upper portion of the main shaft 4 (in the vicinity of the eccentric shaft portion 4a) is supported by a main bearing 12 provided on the frame 11. A sleeve 17 is provided between the main bearing 12 and the main shaft 4 for smoothly rotating the main shaft 4. On the other hand, the lower portion of the main shaft 4 is rotatably supported by a ball bearing 21. The ball bearing 21 is press-fitted and fixed in a bearing housing portion 20 a formed in the center portion of the subframe 20 provided in the lower portion of the sealed container 1. Further, the subframe 20 is provided with a positive displacement oil pump 22. The pump shaft 4 b that transmits the rotational force to the oil pump 22 is formed integrally with one end surface of the main shaft 4. Lubricating oil sucked by the oil pump 22 from the oil reservoir 23 is sent to each sliding portion through an oil hole 4 c formed in the main shaft 4. In FIG. 1, 11a is an oil drain pipe, 18 is a first balancer, 19 is a second balancer, and 8 is a second balancer cover.

Next, the operation of the refrigerant compressor 100 will be described.
In the scroll compressor 100 configured as described above, when a voltage is applied to the electric rotary machine 7, a current flows through the electric wire portion of the stator 2 to generate a magnetic field. This magnetic field works to rotate the rotor 3, and the main shaft 4 is rotationally driven together with the rotor 3. When the main shaft 4 rotates, the slider 16 also rotates in the rocking bearing 13 through the eccentric shaft portion 4a. The rocking scroll 10 whose rotation is suppressed by the Oldham ring 15 performs rocking motion. As a result, part of the refrigerant gas flows into the compression chamber 26 via the suction port (not shown) of the frame 11 and the suction process is started. Further, the remaining part of the refrigerant gas passes through the notch of the steel plate of the stator 2 to cool the electric rotary machine 7 and the lubricating oil.

  The compression chamber 26 moves to the center of the orbiting scroll 10 by the orbiting motion of the orbiting scroll 10, and the volume is further reduced. Through this process, the refrigerant gas sucked into the compression chamber 26 is compressed. At this time, a load is applied to the fixed scroll 9 and the orbiting scroll 10 by the compressed refrigerant gas so as to be separated in the axial direction, and this load is supported by the thrust plate 14 (thrust bearing). The compressed refrigerant passes through the discharge port 9 b of the fixed scroll 9, pushes open the discharge valve 29 that has closed the discharge port 9 b, and flows into the discharge space 33. Then, the gas is discharged from the sealed container 1 through the discharge pipe 25.

In the scroll compressor 100 described above, as shown in FIGS. 2 and 3, a cutout portion in which a part of the outer peripheral surface 16 b is cut out along the cylinder center C direction on the outer peripheral surface 16 b of the slider 16. 16m is formed. The notch portion 16m is formed on the other end side with a first notch portion 16e formed on one end side and a notch cross-sectional area as viewed in the axial center C direction larger than the first notch portion 16e. The second cutout portion 16d and a step portion 16f formed between the first cutout portion 16e and the second cutout portion 16d.
In other words, the second cutout portion 16d located above the step portion 16f has a large cutout sectional area, and the first cutout portion 16e located below the stepped portion has a cutout sectional area. Thereby, the flow passage area when the oil that flows out from the oil hole 4c of the eccentric shaft portion 4a and overflows to the end surface 16c of the slider 16 flows downward through the cutout portion 16m is larger in the second cutout portion 16d. Widely, the first notch 16e below the step 16f is narrow.

In the scroll compressor 100 having the above-described configuration, since the viscosity of the oil is low under a low oil concentration condition, the flow rate of the oil flowing through the notch 16m of the slider 16 is the first notch 16e having a small notch cross-sectional area. Determined by the flow path area. Therefore, in the second cutout portion 16d that is located above the step portion 16f and has a large flow path area, the oil flows down more than the first cutout portion 16e that is located below the step portion 16f and has a small flow passage area. The speed is reduced. Since the second cutout portion 16d has a slower oil flow rate than the first cutout portion 16e, a large amount of oil can be drawn into the sliding portion such as the rocking bearing 13 by the second cutout portion 16d having a low flow velocity. In addition, since the second notch 16d has a wide flow path, the amount of oil present in the second notch 16d itself increases, and the amount of oil supplied to the sliding portion can be increased.

The crowning portion 4d of the eccentric shaft portion 4a and the slider plate 16a have a contact surface 34 (see FIG. 3) in surface contact, and the bearing load is the largest within the range of the contact surface 34. On the other hand, the height direction position of the step portion 16f of the notch portion 16m of the slider 16 is below the range in which the crowning portion 4d of the eccentric shaft portion 4a is in surface contact with the slider plate 16a. More oil can be supplied to the contact surface 34 located above.

By the way, in said Embodiment 1, regarding the wall surface 16h of the 1st notch part 16e in the slider 16, and the wall surface 16g of the 2nd notch part 16d, the shape seen in the axial center C direction of the main axis | shaft 4 is not limited. . However, for example, as in the slider 16A shown in FIG. 4, the outer peripheral surface 16b when the wall surface 16hA of the first notch portion 16e and the wall surface 16gA of the second notch portion 16d are viewed in the direction of the axis C of the main shaft 4. On the other hand, it may be a linear string. A step portion 16fA is formed between the wall surface 16hA and the wall surface 16gA.

Alternatively, like the slider 16B shown in FIG. 5, the wall surface 16gB of the second notch 16d may be formed in a V shape with respect to the outer peripheral surface 16b when viewed in the direction of the axis C of the main shaft 4. A triangular step 16fB is formed between the wall surface 16gB and the linear wall surface 16hB.

  Further, like the slider 16C shown in FIG. 6, the wall surface 16gC of the second notch 16d may be formed in an arc shape with respect to the outer peripheral surface 16b when viewed in the direction of the axis C of the main shaft 4. A semicircular step portion 16fC is formed between the wall surface 16gC and the linear wall surface 16hC.

Regarding the various types of sliders 16A, 16B, and 16C shown in FIGS. 4 to 6 above, the steps 16fA, 16fB, and 16fC are basically provided by providing step portions 16fA, 16fB, and 16fC in the middle of the notch portion 16m. , 16fB, and 16fC, the flow path area is changed, the flow rate is decreased at the upper second cutout portion 16d having a large flow path area, and a large amount of oil is present to increase the amount of oil supplied to the sliding portion. -ing

On the other hand, like the slider 16D shown in FIG. 7, the scroll compressor provided with the surrounding bank part 16k is also contained in this invention. In this scroll compressor, a peripheral bank portion 16k that protrudes upward from the end surface 16c is formed on the outer peripheral edge of the end surface 16c on the other end side of the slider 16D except for the second notch portion 16d. Further, the cutout sectional area of the first cutout portion 4e and the cutout sectional area of the second cutout portion 4d are reduced from the end surface 16c on the other end side of the slider 16 toward the bottom surface on the one end side. The wall surface 16hD of the first cutout portion 4e and the wall surface 16gD of the second cutout portion 4d are formed to be inclined.

According to the scroll compressor using the slider 16D, since the peripheral bank portion 16k is provided on the end surface 16c of the slider 16D, the oil flowing out from the oil hole 4c of the eccentric shaft portion 4a to the end surface 16c of the slider 16D is After staying in the peripheral bank portion 16k, it flows down concentrated on the second notch portion 16d. Therefore, the inside of the second notch 16d can always be filled with a large amount of oil, and the amount of oil supplied to the sliding portion can be further increased. In addition, since the wall surface 16hD of the first notch portion 16e and the wall surface 16gD of the second notch portion 16d are inclined, the other end also in each of the first notch portion 16e and the second notch portion 16d. The closer to the end face 16c on the side, the larger the flow path area and the slower the oil flow rate, so the oil supply amount to the sliding portion can be gradually increased.

1 closed container, 1a middle container, 1b lower container, 1c upper container, 2 stator, 3
Rotor, 4 main shaft (rotary drive shaft), 4a eccentric shaft portion, 4b pump shaft, 4c oil hole, 4d crowning portion, 4e other end surface, 7 electric rotating machine (electric motor), 8 second balancer cover, 9 fixed scroll, 9a Lapping part, 9b Discharge port, 10 Oscillating scroll, 10a Lapping part, 10b Lower surface, 11 Frame, 11a Oil drain pipe, 12 Main bearing, 13 Oscillating bearing, 13a Tube hole, 14 Thrust plate, 15 Oldham ring, 16, 16A, 16B, 16C, 16D Slider, 16a Slider plate, 16b Outer peripheral surface, 16c End surface, 16d Second notch, 16e Second notch, 16f, 16fA, 16fB, 16fC, 16fD Step, 16g, 16gA, 16gB, 16gC, 16gD Wall surface, 16h, 16hA, 16hB, 16hC, 16 D wall surface, 16j bearing hole, 16k peripheral bank portion, 16m cutout portion, 17 sleeve, 18 first balancer, 19 second balancer, 20 subframe, 20a bearing housing portion, 21 ball bearing, 22 oil pump, 23 oil sump 24 suction pipe, 25 discharge pipe, 26 compression chamber, 27 seal, 28 seal, 29 discharge valve, 33 discharge space, 34 contact surface, 100 scroll compressor, C axis.

Claims (5)

A sealed container, a fixed scroll fixedly arranged in the sealed container, a swing scroll that pivots and swings with respect to the fixed scroll to form a compression chamber between the fixed scroll, and the swing scroll A cylindrical rocking bearing provided upright on the surface opposite to the surface facing the fixed scroll, and a long hole bearing that is inserted into the cylindrical hole of the rocking bearing and is slidably supported. A cylindrical slider having a hole, a rotary drive shaft having an oil hole fixed in a motor rotor disposed in the hermetic container and penetrating in an axial direction, and one end surface of the rotary drive shaft. And an oil pump for pumping the lubricating oil in the sealed container into the oil hole, and is formed at a position eccentric from the axis of the rotary drive shaft on the other end surface of the rotary drive shaft, and is installed in the bearing hole of the slider. An eccentric shaft portion that is slidably supported and has an oil hole from the rotational drive shaft, and a cutout portion formed by cutting out a part of the outer peripheral surface of the slider along the cylinder center direction. Comprising
The cutout portion includes a first cutout portion formed on one end side, and a second cutout portion formed on the other end side with a larger cutout cross-sectional area as viewed in the axial direction than the first cutout portion. A scroll compressor comprising a cutout portion, wherein a step portion is provided between the first cutout portion and the second cutout portion. The notch cross-sectional area of the first notch part or the notch cross-sectional area of the second notch part is formed so as to decrease from the other end side of the slider toward the one end side. Scroll compressor described in 1. A slider plate disposed between the inner peripheral surface of the bearing hole of the slider and the outer peripheral surface of the eccentric shaft portion; and the slider bulges radially outward from the outer peripheral surface of the eccentric shaft portion facing the slider plate. A crowning portion in contact with the plate,
The step portion of the slider is formed at a position farther from an end surface on the other end side of the slider than a contact surface between the slider plate and the crowning portion. Scroll compressor. The wall surface of the cutout portion of the slider is formed in a straight line shape, a V shape or an arc shape when viewed in the axial direction of the rotary drive shaft. The scroll compressor according to one item. The scroll compression according to any one of claims 1 to 4, wherein a peripheral bank portion is formed on an outer peripheral edge of the end surface on the other end side of the slider excluding the second cutout portion. Machine.

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