CN109519372B - One-way bearing assembly, oil brake device and scroll compressor - Google Patents
One-way bearing assembly, oil brake device and scroll compressor Download PDFInfo
- Publication number
- CN109519372B CN109519372B CN201710847868.9A CN201710847868A CN109519372B CN 109519372 B CN109519372 B CN 109519372B CN 201710847868 A CN201710847868 A CN 201710847868A CN 109519372 B CN109519372 B CN 109519372B
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- Prior art keywords
- rollers
- outer race
- way bearing
- stop
- rotating shaft
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- 238000006073 displacement reaction Methods 0.000 claims abstract description 39
- 230000006835 compression Effects 0.000 claims description 23
- 238000007906 compression Methods 0.000 claims description 23
- 230000002093 peripheral effect Effects 0.000 claims description 9
- 239000012530 fluid Substances 0.000 claims description 6
- 230000007246 mechanism Effects 0.000 claims description 6
- 230000000717 retained effect Effects 0.000 claims description 5
- 230000001360 synchronised effect Effects 0.000 claims description 4
- AZDRQVAHHNSJOQ-UHFFFAOYSA-N alumane Chemical group [AlH3] AZDRQVAHHNSJOQ-UHFFFAOYSA-N 0.000 claims description 3
- 238000005299 abrasion Methods 0.000 abstract description 10
- 239000003921 oil Substances 0.000 description 100
- 230000002441 reversible effect Effects 0.000 description 17
- 208000035874 Excoriation Diseases 0.000 description 9
- 230000002829 reductive effect Effects 0.000 description 9
- 239000003507 refrigerant Substances 0.000 description 8
- 230000000670 limiting effect Effects 0.000 description 5
- 239000010687 lubricating oil Substances 0.000 description 4
- 238000005192 partition Methods 0.000 description 4
- 238000009434 installation Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000036961 partial effect Effects 0.000 description 3
- 208000010392 Bone Fractures Diseases 0.000 description 2
- 206010017076 Fracture Diseases 0.000 description 2
- 230000002238 attenuated effect Effects 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 239000012634 fragment Substances 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000003313 weakening effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/28—Safety arrangements; Monitoring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
Abstract
The present invention relates to a one-way bearing assembly. The one-way bearing assembly includes: an outer ring; an annular retainer provided inside the outer ring; a plurality of rollers held in the cage; and a plurality of springs held on the cage with ends of the springs in contact with the respective rollers. The one-way bearing assembly also includes at least one stop mounted concentric with the outer race, the stop being configured to limit radial displacement of the plurality of rollers. The unidirectional bearing assembly of the invention can reduce the deformation amount of the spring so as to avoid abrasion or fracture of the spring. The invention also relates to an oil brake device and a scroll compressor with the oil brake device.
Description
Technical Field
The invention relates to a one-way bearing assembly, an oil brake device with the one-way bearing assembly and a scroll compressor with the oil brake device.
Background
The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.
Scroll compressors are a type of compression machine that compress in a positive displacement manner. During operation of the scroll compressor, power of the motor is transmitted to the scroll assembly via the rotation shaft to cause relative rotation of the scroll assembly, thereby achieving compression of refrigerant. In this process, the rotation shaft rotates in the design direction (i.e., forward direction).
However, when the scroll compressor is stopped or de-energized during normal operation, high pressure gas flowing back into the scroll assembly from the high pressure side of the scroll compressor or high pressure gas already present in the scroll assembly may cause the scroll assembly to reverse due to a pressure difference between the high pressure side and the low pressure side of the scroll compressor, thereby driving the rotation shaft to reverse. The reversal of the rotation axis within the scroll compressor will produce a large reverse current and reverse voltage, which may burn the motor and inverter. Accordingly, there is a need for a device that prevents or reduces reverse rotation of a scroll compressor at shutdown.
Disclosure of Invention
The present invention aims to address one or more of the above problems.
An object of the present invention is to provide an oil brake apparatus capable of preventing or reducing reverse rotation of a scroll compressor at the time of shutdown, the oil brake apparatus being provided with a one-way bearing. When the rotating shaft in the scroll compressor rotates in the forward direction, the rotating shaft can rotate relative to the outer race of the one-way bearing and the rollers. When the rotating shaft in the vortex compressor reversely rotates, the outer ring of the one-way bearing and the rotating shaft synchronously rotate, so that the disturbance of lubricating oil in an oil pool at the bottom of the compressor shell is increased, and the reverse rotating speed of the rotating shaft is quickly attenuated. Another object of the present invention is to reduce the amount of deformation of the spring of the one-way bearing during normal operation of the scroll compressor by limiting radial displacement of the roller of the one-way bearing during normal operation of the scroll compressor, thereby avoiding wear or breakage of the spring and thus avoiding wear or damage to other parts of the scroll compressor by debris generated when the spring wears or breaks.
One aspect of the present invention is to provide a one-way bearing assembly adapted to be mounted to a rotating shaft. The one-way bearing assembly includes: the inner peripheral surface of the outer ring is provided with a plurality of wedge-shaped groove parts, and each wedge-shaped groove part comprises a wide end and a narrow end; the annular retainer is arranged inside the outer ring; a plurality of rollers held in the cage; and a plurality of springs retained on the cage and having ends in contact with the respective rollers to bias the rollers toward the narrow ends. When the one-way bearing assembly is mounted to the rotating shaft, the plurality of rollers are movable in the circumferential direction of the outer race in the corresponding wedge-shaped groove portions of the outer race between a first position at the wide end, at which the rotating shaft is rotatable relative to the outer race and the rollers, the springs experience a maximum amount of deformation, and the plurality of rollers have a maximum inscribed circle of diameter D1, and a second position at which the rollers are engaged between the outer race and the rotating shaft to enable synchronous rotation of the outer race with the rotating shaft, the springs experience a minimum amount of deformation, and the plurality of rollers have a minimum inscribed circle of diameter D2, wherein D2 is less than D1.
The rotating shaft moves the plurality of rollers from the second position toward the first position in the corresponding wedge-shaped groove portions of the outer race when the rotating shaft rotates in a first direction, and moves the plurality of rollers toward the second position in the corresponding wedge-shaped groove portions of the outer race when the rotating shaft rotates in a second direction opposite to the first direction.
The one-way bearing assembly further includes at least one stop mounted concentric with the outer race, the at least one stop being designed to limit circumferential positions of the plurality of rollers between a first position and a second position when the rotating shaft rotates in the first direction.
In one embodiment, the at least one stop is mounted stationary relative to the outer race, the at least one stop having an inner diameter less than D1 and greater than D2.
In one embodiment, the at least one stop is fixed on the rotation shaft, the outer diameter of the at least one stop being arranged such that the spacing s between the outer periphery of the at least one stop and the inner wall of the bearing mount fitted on the outer ring is less than half the difference between D1 and D2.
In one embodiment, the at least one stop is designed such that the maximum radial displacement L of the plurality of rollers, when the rotation shaft rotates in the first direction, satisfies the following relationship with D1, D2: l=0.5× (D1-D2) ×a, where a is greater than 0 and less than 1.
In one embodiment, the at least one stopper is mounted to be fixed with respect to the outer race such that a separation distance between an inner circumferential surface of the at least one stopper and an outer circumferential surface of the rotating shaft is equal to the maximum radial displacement L.
In one embodiment, the at least one stop is fixed to the rotating shaft, and when the radial displacement of the plurality of rollers reaches a maximum radial displacement L, the at least one stop is blocked so that the radial displacement of the plurality of rollers cannot be further increased.
In one embodiment, a is a value between 0.01 and 0.2.
In one embodiment, the at least one stop is disposed at a longitudinal end of the outer race. Preferably, the at least one stop is in contact with a longitudinal end of the outer race.
In one embodiment, the at least one stop includes a first stop mounted above the longitudinal upper end of the outer race and a second stop mounted below the longitudinal lower end of the outer race.
In one embodiment, the stop is an aluminum ring.
Another aspect of the present invention is to provide an oil brake apparatus adapted to be mounted to a rotating shaft. The oil brake device comprises: a body portion having a central through hole; and one or more oil brake wings extending radially outwardly from the body portion. The oil brake apparatus further includes a one-way bearing assembly according to the present invention positioned in the central throughbore and the outer race is press fit in the central throughbore.
Preferably, the one or more oil brake wings are integrally formed with the body portion.
In one embodiment, the outer race is press fit in the central through bore via a bearing mount.
In one embodiment, at least one stop is press fit within the bearing mount.
A further aspect of the present invention is to provide an oil brake apparatus adapted to be mounted to a rotating shaft, and comprising: a body portion having a central through hole; and one or more oil brake wings extending radially outwardly from the body portion. The oil brake device also comprises a one-way bearing which is in press fit in the central through hole. The one-way bearing includes: the inner peripheral surface of the outer ring is provided with a plurality of wedge-shaped groove parts, and each wedge-shaped groove part comprises a wide end and a narrow end; the annular retainer is arranged inside the outer ring; a plurality of rollers held in the cage; and a plurality of springs retained on the cage with ends of the plurality of springs contacting the respective rollers to bias the rollers toward the narrow ends. When the oil brake apparatus is mounted to the rotating shaft, the plurality of rollers are movable in the circumferential direction of the outer race in the corresponding wedge-shaped groove portions of the outer race between a first position at the wide end, at which the rotating shaft is rotatable relative to the outer race and the rollers, the springs are subjected to a maximum deformation amount, and the plurality of rollers have a maximum inscribed circle with a diameter D1, and a second position at which the rollers are engaged between the outer race and the rotating shaft to enable the outer race to rotate in synchronization with the rotating shaft, the springs are subjected to a minimum deformation amount, and the plurality of rollers have a minimum inscribed circle with a diameter D2, wherein D2 is smaller than D1.
The rotating shaft moves the plurality of rollers from the second position toward the first position in the corresponding wedge-shaped groove portions of the outer race when the rotating shaft rotates in a first direction, and moves the plurality of rollers toward the second position in the corresponding wedge-shaped groove portions of the outer race when the rotating shaft rotates in a second direction opposite to the first direction.
Preferably, the one or more oil brake wings are integrally formed with the body portion.
In one embodiment, the one-way bearing is press-fitted in the central through hole via the bearing mount, and at least one stopper for restricting circumferential displacement or radial displacement of the plurality of rollers, which is mounted concentrically with the outer race, is provided in the central through hole.
In one embodiment, the at least one stop is mounted stationary relative to the outer race and the at least one stop has an inner diameter less than D1 and greater than D2.
In one embodiment, the at least one stop is fixed to the rotating shaft and an outer diameter of the at least one stop is configured such that a maximum radial displacement of the plurality of rollers is less than half a difference between D1 and D2.
Yet another aspect of the present invention is to provide a scroll compressor including the oil brake apparatus according to the present invention.
The present invention also provides a scroll compressor comprising: the compression mechanism is used for compressing working fluid and comprises a fixed scroll and an movable scroll; a rotation shaft driving the movable scroll; a motor driving the rotation shaft to rotate in a first direction; and an oil brake device mounted on the rotating shaft. The oil brake device comprises: a body portion having a central through hole; and one or more oil brake wings extending radially outwardly from the body portion.
The oil brake device also comprises a one-way bearing which is in press fit in the central through hole. The one-way bearing includes: the inner peripheral surface of the outer ring is provided with a plurality of wedge-shaped groove parts, and each wedge-shaped groove part comprises a wide end and a narrow end; the annular retainer is arranged inside the outer ring; a plurality of rollers held in the cage; and a plurality of springs retained on the cage and having ends in contact with the respective rollers to bias the rollers toward the narrow ends. The plurality of rollers are movable in corresponding wedge grooves of the outer race between a first position at the wide end and a second position at the narrow end. In the first position, the rotating shaft is rotatable relative to the outer race and the rollers, the springs experience a maximum amount of deformation, and the plurality of rollers have a maximum inscribed circle of diameter D1. In the second position, the rollers are engaged between the outer race and the rotating shaft to enable the outer race to rotate in synchronization with the rotating shaft, the springs are subject to a minimal amount of deformation, and the plurality of rollers have a minimal inscribed circle with a diameter D2, wherein D2 is less than D1.
When the rotating shaft rotates in a first direction, the rotating shaft moves the plurality of rollers from the second position toward the first position in the corresponding wedge-shaped groove portions of the outer race. When the rotating shaft rotates in a second direction opposite the first direction, the rotating shaft moves the plurality of rollers toward the second position in the corresponding wedge-shaped groove portion of the outer race.
The oil brake apparatus further includes at least one stopper fixed to the rotating shaft and located in the central through hole. The at least one stop is designed to limit the circumferential position of the plurality of rollers between the first position and the second position when the rotating shaft rotates in the first direction.
In one embodiment, the one-way bearing is press-fit in the central through hole via a bearing mount.
The invention limits the radial displacement of the roller of the one-way bearing by limiting the moving distance between the rotating shaft of the scroll compressor and the oil brake device, thereby reducing the deformation of the spring. The invention does not need to modify the structure of the unidirectional bearing, so that the unidirectional bearing assembly with better applicability is provided and can be applied to various unidirectional bearings.
By the invention, the deformation quantity of the spring of the one-way bearing during normal operation of the scroll compressor can be effectively limited, the abrasion of the spring and the risk of fracture of the spring are reduced, and the risk of abrasion or damage to other parts of the scroll compressor caused by fragments generated during abrasion and fracture of the spring is also reduced. This allows the oil brake to function properly and extends its useful life.
Drawings
Embodiments of the invention will hereinafter be described, by way of example only, with reference to the accompanying drawings, in which like features or elements are indicated with like reference numerals and in which:
fig. 1 is a sectional view of a scroll compressor according to a first embodiment of the present invention;
FIG. 2 is a top view of the oil brake apparatus shown in FIG. 1;
FIG. 3 is a cross-sectional view taken along line A-A in FIG. 2;
FIG. 4 is a partial cross-sectional view of a one-way bearing used in the oil brake apparatus shown in FIG. 2;
FIG. 5 is a schematic illustration of the operation of a one-way bearing used in the oil brake apparatus of FIG. 2;
FIG. 6 is an enlarged view of a portion of the one-way bearing shown in FIG. 5, wherein the spring is at a maximum compression;
FIG. 7 is another enlarged partial view of the one-way bearing of FIG. 5, wherein the spring is at a minimum amount of compression;
FIG. 8 is a top view of an oil brake apparatus of a scroll compressor in accordance with a second embodiment of the present invention;
FIG. 9 is a cross-sectional view taken along line B-B in FIG. 8;
FIG. 10 is an enlarged view of a portion of FIG. 9;
FIGS. 11-12 are perspective and top views of a stop member used in the oil brake apparatus shown in FIG. 8;
fig. 13 is a sectional view showing an oil brake apparatus of a scroll compressor according to a third embodiment of the present invention;
FIG. 14 is an enlarged partial view of the cross-sectional view of FIG. 13;
fig. 15-16 are perspective and top views of a stop member for use with the oil brake apparatus shown in fig. 13.
Detailed Description
The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. It should be understood that throughout the drawings, like reference numerals refer to the same or like parts and features. The drawings are merely schematic representations, not necessarily showing specific dimensions and proportions of the various embodiments of the invention, the relative details or structure of the various embodiments of the invention, which may be shown exaggerated in the particular figures or specific parts of the drawings.
Fig. 1 shows an exemplary cross-sectional view of a scroll compressor according to a first embodiment of the present invention. As shown in fig. 1, the scroll compressor includes a housing S1, a base S2, a top cover S3, and a partition plate S4 provided between the housing S1 and the top cover S3. The casing S1 is provided with an intake port 1 for sucking refrigerant (working fluid), and the top cover S3 is provided with a discharge port for discharging refrigerant
An exhaust port 2 (of the working fluid). The internal space of the scroll compressor is partitioned into a high pressure side and a low pressure side by a partition plate S4. Specifically, the space enclosed by the housing S1, the base S2, and the partition plate S4 constitutes a low pressure side for sucking a refrigerant (working fluid) of low pressure. The space enclosed by the partition plate S4 and the top cover S3 constitutes a high-pressure side for discharging the compressed high-pressure refrigerant (working fluid). The housing S1 houses an orbiting scroll 3 and a fixed scroll 4 as compression mechanisms or scroll assemblies, and a motor 6 and a rotary shaft 5 as driving mechanisms.
In operation, refrigerant enters the scroll compressor from its suction port 1 and enters the respective compression chambers formed by the orbiting scroll 3 and the non-orbiting scroll 4. Power is transmitted from the motor 6 to the movable scroll 3 via the rotation shaft 5, so that the movable scroll 3 makes translational motion with respect to the fixed scroll 4 (i.e., the center axis of the movable scroll 3 revolves around the center axis of the fixed scroll 4, but the movable scroll 3 itself does not rotate around its own center axis), compression of refrigerant is achieved, and compressed refrigerant is discharged through the discharge port 2.
However, when the scroll compressor is stopped or de-energized during normal operation, high pressure gas flowing back into the scroll assembly from the high pressure side of the scroll compressor or high pressure gas already present in the scroll assembly may cause the scroll assembly to reverse, thereby reversing the rotation shaft 5. The reversal of the rotation shaft 5 in the scroll compressor will generate a large reverse current and reverse voltage, which may burn out the motor 6 and the inverter (not shown in the figures).
In order to prevent or reduce the reverse rotation of the scroll compressor at the time of shutdown, the inventors proposed a scheme in which an oil brake is provided to rapidly consume the pressure difference energy between the high pressure side and the low pressure side by using the resistance of the lubricating oil OL in the oil sump at the bottom of the scroll compressor housing, thereby rapidly attenuating the reverse rotation speed of the rotating shaft to zero.
More specifically, as an example, as shown in fig. 1, an oil brake 10 is provided on the rotary shaft 5.
Fig. 2 shows a top view of the oil brake apparatus 10, and fig. 3 shows a cross-sectional view of the oil brake apparatus 10 taken along line A-A of fig. 2. As shown in fig. 3, the oil brake apparatus 10 includes a body portion 11, two oil brake wings 12 arranged radially symmetrically, a one-way bearing 14, and a bearing mount 15. The oil brake wing 12 is integrally formed with the body portion 11. The body portion 11 has a central through hole 13. For ease of installation, the one-way bearing 14 is press-fitted in the central through hole 13 via the bearing mount 15. However, the invention is not limited thereto, in other possible embodiments the one-way bearing 14 may also be press-fitted directly into the central through hole 13, in which case the oil brake device may omit the bearing mount. Referring also to fig. 4-5, the one-way bearing 14 includes an outer race 131, a plurality of rollers, a plurality of springs 133, and a cage 134 for holding the rollers and springs 133. In the present embodiment, the rollers are in the form of the needle rollers 132, but the present invention is not limited thereto, and in other embodiments, the rollers may be in the form of balls. Outer race 131 has a central axis O. The spring 133 is formed by oppositely bending both ends of a leaf spring having a certain width, and its cross section is substantially in the shape of a staple, as shown in fig. 4. The two ends 133a, 133b of the spring 133 respectively abut against the needle roller 132. The one-way bearing 14 is press-fitted in the central through hole 13 via the bearing mount 15, the rotary shaft 5 passes through the center of the one-way bearing 14, and the needle rollers 132 are in contact with the rotary shaft 5 and the outer race 131. One skilled in the art can envisage further arranging an inner race in the one-way bearing 14 to hold the needle rollers 132 and springs 133 between the inner race and the outer race 131, and the rotary shaft 5 can be fitted in the one-way bearing 14 via the inner race.
The operation of the oil brake apparatus 10 will be described with reference to fig. 5-7. As shown in fig. 5, the inner peripheral wall of the outer race 131 is provided with a plurality of wedge-shaped groove portions 135 distributed in the circumferential direction. A set of needles 132 and springs 133 are disposed in each wedge groove 135. When the oil brake apparatus 10 is mounted on the rotary shaft 5, the needle rollers 132 are located between the respective wedge-shaped groove portions and the rotary shaft 5 and are in loose or rolling contact with the same or in wedging or locking contact with the same depending on the rotation direction of the rotary shaft 5 to realize the function of the one-way clutch.
When the scroll compressor is in normal operation, the rotation shaft 5 is rotated in the forward direction as indicated by an arrow M1 in fig. 5 and 6, and the oil brake 10 is also slowly rotated in the forward direction with the rotation shaft 5 by a small amount of friction force as indicated by an arrow M2 in fig. 5. The rotation shaft 5 presses a portion of the needle roller 132 radially outwardly so that the needle roller 132 moves toward the first position P1 in the direction M1 on the corresponding wedge groove 135 against the urging force of the spring 133. As shown in fig. 6, at the position P1, the spring 133 is at the maximum compression amount, and the needle roller 132 abuts on the outer ring 131 without locking with the rotation shaft 5, and the rotation shaft 5 can rotate relative to the outer ring 131. When the needle 132 is at position P1, the spring 133 is at a maximum compression, and the needle 132 has a maximum inscribed circle with a diameter D1, as shown by the broken line in fig. 6. On the other hand, since the oil brake wings 12 of the oil brake 10 are subjected to the resistance of the lubricating oil OL in the oil sump at the lower portion of the scroll compressor 1, the rotation speed of the outer ring 131 is far lower than that of the rotation shaft 5, and the outer ring 131 is not synchronized with the rotation of the rotation shaft 5, and at this time, the oil brake 10 is not active.
When the scroll compressor is shut down or de-energized during normal operation, as previously described, the high pressure side gas is caused to flow back into the scroll assembly due to the pressure differential between the high pressure side and the low pressure side within the scroll compressor, causing the rotating shaft to rotate in the opposite direction M3. At this time, the needle roller 132 moves from the wide end position P1 toward the narrow end position P2 in the direction M3 on the corresponding wedge groove portion 135 by the rotation shaft 5 and the spring 133. As shown in fig. 7, when the needle roller 132 moves to the position P2, the needle roller 132 is caught or wedged between the rotation shaft 5 and the outer ring 131, so that the outer ring 131 rotates in synchronization with the rotation shaft 5, and the one-way bearing 14 locks with the rotation shaft 5. When the needle 132 is in position P2, the spring 133 is at a minimum compression, and the needle 132 has a minimum inscribed circle with a diameter D2, where D2 is less than D1. When the one-way bearing 14 is locked with the rotary shaft 5, the needle roller is engaged between the outer circumferential surface of the rotary shaft 5 and the corresponding wedge-shaped groove portion 135 of the outer ring 131, and therefore the minimum inscribed circle of the needle roller coincides with the outer circumferential surface of the rotary shaft 5, and the diameter D2 is also the diameter of the rotary shaft 5. Since the one-way bearing 14 is press-fitted into the central through hole 13 of the oil brake apparatus 10 via the bearing mount 15, locking of the one-way bearing 14 with the rotation shaft 5 causes the entire oil brake apparatus 10 to rotate in synchronization with the rotation shaft 5, and the oil brake wings 12 rapidly agitate the oil pool at the bottom of the scroll compressor. Due to the large resistance of the lubricant OL, the speed of the reverse rotation of the rotation shaft 5 is rapidly attenuated to zero, thereby suppressing or weakening the reverse rotation of the rotation shaft, avoiding the generation of large reverse current and reverse voltage and thereby preventing the damage of the components of the scroll compressor.
However, the inventors further found that during the operation of the oil brake apparatus constructed as described above, the needle roller 132 compresses the spring 133 during normal operation of the compressor, the spring 133 undergoes a large compression amount, so that the spring 133 is easily worn out, and there is also a risk of breakage occurring. Once the spring 133 is worn seriously or broken, the one-way bearing 13 loses its original function, so that the oil brake cannot function to prevent the rotation shaft from being reversed when the scroll compressor is stopped or powered off during normal operation, resulting in damage to the motor or the inverter, etc. On the other hand, debris generated when the spring 133 wears and breaks may enter other components of the scroll compressor with the oil, causing other compressor parts to wear or fail.
The inventors have also found that a smaller radial displacement of the roller will cause a larger circumferential displacement, the amount of compression of the spring being more sensitive to the amount of radial displacement of the roller. Based on such findings, the present inventors have further proposed an inventive concept of reducing the amount of deformation of the spring of the oil brake device when the scroll compressor is operated by limiting the radial displacement of the roller to reduce the risk of spring wear and breakage.
An oil brake apparatus 20 of a scroll compressor according to a second embodiment of the present invention will be described in detail with reference to fig. 8 to 12.
Similar to the oil brake apparatus 10 described above, the oil brake apparatus 20 includes a body portion 21, two oil brake wings 22 arranged radially symmetrically, a one-way bearing 24, and a bearing mount 25. The oil brake wing 22 is integrally formed with the body portion 21. The body portion 21 has a central through hole 23. For ease of installation, the one-way bearing 24 is press-fitted in the central through hole 23 via the bearing mount 25. As mentioned above, in other possible embodiments of the invention, the one-way bearing 24 may also be press-fitted directly into the central through hole 23, in which case the oil brake device may omit the bearing mount. It should be noted here that although in the first and second embodiments shown, the oil brake device has two oil brake wings, the present invention is not limited thereto. The oil brake device may be provided with only one oil brake wing, or the oil brake device may be provided with a plurality of oil brake wings extending radially outwardly from the body portion and equally spaced along the circumference of the body portion. In addition, in order to more clearly illustrate the inventive concept of the present invention, in the present second embodiment, the structure of the one-way bearing 24 is the same as that of the one-way bearing 14 of the oil brake apparatus 10, including an outer race 231, a plurality of rollers, a plurality of springs, and a cage for holding the rollers and springs, the one-way bearing 24 is press-fitted in the central through hole 23 via the bearing mount 25 and is provided on the rotating shaft 5, the rollers (e.g., needle rollers) are in contact with the rotating shaft 5 and the outer race 231, the springs are held on the cage against the rollers, and the rollers move in the corresponding wedge-shaped groove portions of the outer race 231. The invention is not limited thereto and the oil brake apparatus of the invention may include other configurations of one-way bearings.
The oil brake apparatus 20 also includes at least one stop. The one-way bearing 24 and the at least one stop constitute a one-way bearing assembly according to one embodiment of the invention. In the second embodiment shown in fig. 8 to 12, the oil brake apparatus 20 includes two stoppers, i.e., an upper stopper 26 and a lower stopper 27. The upper stopper 26 and the lower stopper 27 have the same central axis O as the outer race 25. However, the present invention is not limited thereto, and the oil brake apparatus 20 may include more stoppers or only one stopper. In the present embodiment, the upper stopper 26 and the lower stopper 27 are aluminum rings. Alternatively, the upper and lower stoppers 26 and 27 may be made of other materials.
As shown in fig. 10, the upper stopper 26 and the lower stopper 27 are press-fitted in the bearing mount 25, the upper stopper 26 being located above the upper end of the outer race 231 of the one-way bearing 24, and the lower stopper 27 being located below the lower end of the outer race 231 of the one-way bearing 24. The upper and lower stoppers 26 and 27 may be spaced apart from the upper and lower ends of the outer race 231, respectively. Alternatively, the upper and lower stoppers 26 and 27 may also be respectively in contact with the upper and lower ends of the outer race 231, so that the height of the body portion 21 may be reduced, thereby making the oil brake apparatus 20 more compact.
In the present second embodiment, the upper stopper 26 and the lower stopper 27 may have the same structure and size, but the present invention is not limited thereto, and in other embodiments, the upper stopper 26 and the lower stopper 27 may have different sizes, for example, have different thicknesses. In the following description, only the upper stopper 26 will be described.
Fig. 11 and 12 show a perspective view and a top view, respectively, of the upper limiter 26. As shown in fig. 12, in the oil brake apparatus 20 according to the second embodiment of the present invention, the upper stopper 26 has an inner diameter d1 and an outer diameter d2. As described above, when the compressor is normally operated, the spring is at the maximum compression amount, and at this time, the diameter of the maximum inscribed circle of the roller is D1, and when the compressor is stopped or powered off during normal operation, the one-way bearing is locked with the rotating shaft, and the oil brake device is rotated in synchronization with the rotating shaft, and at this time, the diameter of the minimum inscribed circle of the roller is D2. The inner diameter D1 of the upper stopper 26 is set to be larger than D2 and smaller than D1. Specifically, D1 satisfies the following relationship with D1 and D2: d1 =d2+ (D1-D2) n, n is less than 1. In the second embodiment, n is a number between 0.01 and 0.2. But the present invention is not limited thereto. The value of n can be set according to specific needs. For example, n may be set to a suitable value according to the rotational speed of the rotation shaft at the time of normal operation of the scroll compressor, the elastic modulus of the spring, and the like. With the above arrangement, when the rotation shaft rotates in the forward direction, the maximum displacement of the rotation shaft that can move in the radial direction will be limited by the inner diameter D1 (< D1) of the upper stopper 26, whereas when the rotation shaft rotates in the reverse direction, the maximum displacement of the rotation shaft that can move in the radial direction is still limited by the diameter D2 of the minimum inscribed circle of the roller, as in the first embodiment. Thus, with a specific setting of the inner diameter D1 of the upper limit piece 26, the maximum radial displacement of the rotating shaft 5 can be limited to half the difference between D1 and D2, i.e. such that the maximum radial displacement of the rotating shaft 5 is less than half the difference between D1 and D2, such that the maximum radial displacement L of the roller is also limited to less than half the difference between D1 and D2. Considering the slope of the wedge groove, a small amplitude reduction in radial displacement of the roller will greatly reduce the amplitude of circumferential displacement of the roller, thereby reducing the amount of compression of the spring, thereby preventing or reducing the likelihood of wear and breakage of the spring.
The above arrangement is equally applicable to the lower limiting member 27. By the above arrangement of the upper and lower stoppers 26 and 27, when the rotation shaft 5 moves radially in the normal operation of the scroll compressor to come into contact with the upper and lower stoppers 26 and 27, the upper and lower stoppers 26 and 27 restrict the rotation shaft 5 from further radially displacing, thereby restricting the rotation shaft from further pressing the roller and thus restricting the roller from further compressing the spring, so that the compression amount of the spring is reduced, the risk of abrasion and breakage of the spring is reduced, and generation of chips causing abrasion or damage to other parts of the scroll compressor due to abrasion or breakage of the spring can be avoided.
In the second embodiment shown in fig. 8 to 12, the upper stopper 26 and the lower stopper 27 are press-fitted in the bearing mount 25 of the oil brake apparatus 20, and the outer diameter d2 of the upper stopper 26 and the lower stopper 27 is slightly larger than or equal to the inner diameter of the bearing mount 25 at the stopper mount. Alternatively, the upper and lower stoppers 26 and 27 may be provided to be press-fitted directly into the central through hole 23 of the oil brake apparatus, and the outer diameters d2 of the upper and lower stoppers 26 and 27 may be slightly larger than or equal to the diameter of the central through hole 23 of the oil brake apparatus 20.
Fig. 13 to 16 show an oil brake apparatus 30 of a scroll compressor according to a third embodiment of the present invention. The oil brake 30 comprises a body portion 31, two oil brake wings 32 arranged radially symmetrically, a one-way bearing 34, a bearing mount 35 and at least one stop. The one-way bearing 34 and the at least one stop constitute a one-way bearing assembly according to another embodiment of the invention. The oil brake wing 32 is integrally formed with the body portion 31. The body portion 31 has a central through hole 33. For ease of installation, the one-way bearing 34 is press-fitted in the central through hole 33 via the bearing mount 35. As mentioned above, in other possible embodiments of the invention, the one-way bearing 34 may also be press-fitted directly into the central through hole 33, in which case the oil brake device may omit the bearing mount. The oil brake apparatus 30 is generally similar in structure to the oil brake apparatus 20 except that the stopper is provided on the rotation shaft 5 instead of being press-fitted in the body portion of the oil brake apparatus. The same parts as those of the oil brake apparatus of the previous embodiment will not be repeated herein, and only the differences will be described in detail hereinafter.
As shown in fig. 13, the upper stopper 36 and the lower stopper 37 are engaged with the rotation shaft 5, and are respectively located above the upper end and below the lower end of the outer ring 331 of the one-way bearing 34. The upper and lower stoppers 36 and 37 may be spaced apart from upper and lower ends of the outer ring 331, respectively. Alternatively, the upper stopper 36 and the lower stopper 37 may also be in contact with the upper end portion and the lower end portion of the outer race 331, respectively, so that the height of the body portion 31 may be reduced, thereby making the oil brake apparatus 30 more compact.
Fig. 15 and 16 are a perspective view and a plan view, respectively, showing a stopper of an oil brake apparatus 30 of a scroll compressor according to a third embodiment of the present invention. In the present third embodiment, the upper stopper 36 and the lower stopper 37 may have the same structure and size. The present invention is not limited thereto and the upper stopper 36 and the lower stopper 37 may have different sizes. Only the upper limit stop 36 will now be described.
As shown in fig. 16, the upper stopper 36 has an inner diameter d3 and an outer diameter d4. The upper stopper 36 is fixed to the rotation shaft 5, and thus, its inner diameter d3 is set to be the same as or slightly smaller than the outer diameter of the rotation shaft 5. As shown in fig. 14, the upper stopper 36 is press-fitted in the bearing mount 35, and the outer diameter d4 of the upper stopper 36 is set such that there is a space s between the outer periphery of the upper stopper 36 and the inner wall of the bearing mount 35. Alternatively, the upper stopper 36 may be press-fitted directly into the central through hole 33, with the outer diameter d4 of the upper stopper 36 being set such that there is a space s between the outer periphery of the upper stopper 36 and the inner wall of the central through hole 33.
The spacing s is less than half the difference between D1 and D2 to enable reduced displacement of the rollers in the radial direction during normal operation of the scroll compressor. Specifically, the outer diameter D4 of the upper stopper 36 is set so that the following relationship is satisfied between the spacing s and D1, D2: s=0.5 (D1-D2) m, m being smaller than 1. In the third embodiment, m is a number between 0.01 and 0.2. But the present invention is not limited thereto. The value of m can be set according to specific needs. For example, m may be set to a suitable value according to the rotation speed of the rotation shaft at the time of normal operation of the scroll compressor, the elastic modulus of the spring, and the like.
The above arrangement is equally applicable to the lower stopper 37. With the above-described arrangement of the upper stopper 36 and the lower stopper 37, when the rotary shaft 5 is radially displaced in normal operation of the scroll compressor, the maximum radial displacement thereof is limited to the spacing s, and the maximum radial displacement L of the rollers is also limited to s. That is, the maximum radial displacement of the rotation shaft 5 and the maximum radial displacement L of the roller are both limited to less than half the difference between D1 and D2. When the radial displacement of the plurality of rollers reaches the maximum radial displacement L, at least one stopper is blocked by the bearing mount 35 or the body portion 31, so that the radial displacement of the plurality of rollers cannot be further increased. Accordingly, the rollers are not pressed to the positions P1 on the corresponding wedge grooves on the outer ring 331, the compression amount of the springs is reduced, the risk of abrasion and breakage of the springs is reduced, and generation of chips causing abrasion or damage to other parts of the scroll compressor due to abrasion or breakage of the springs can be avoided.
The first to third embodiments of the present invention are described above. Neither the second nor the third embodiment described above makes any modification to the structure of the one-way bearing itself shown in the first embodiment, and reduces the amount of compression of the spring by limiting the radial displacement of the rollers during normal operation of the rotary compressor by only providing a limiter on the body portion of the oil brake device or on the rotary shaft, reducing the risk of wear and breakage of the spring. However, the present invention is not limited thereto. In other possible embodiments, the circumferential displacement of the rollers may also be limited by modifying the structure of the one-way bearing. For example, a stopper may be provided on the inner peripheral surface of the bearing outer race to limit the moving distance of the roller on the corresponding wedge groove portion, thereby reducing the compression amount of the spring.
In the second and third embodiments described above, the stopper takes the form of a ring. But the present invention is not limited thereto. In other possible embodiments, other forms of stop may be used, provided that the inner or outer diameter of the stop is sufficient to limit radial or circumferential displacement of the roller.
In the embodiment shown above, the spring in the one-way bearing of the oil brake is a leaf spring of generally staple shape, which spring is subject to compression. However, the present invention is not limited thereto, and the spring in the one-way bearing of the oil brake device may be other forms of compression springs, for example, the spring may be an N-shaped spring or a W-shaped spring. In addition, the inventive concept of the present invention is equally applicable to a one-way bearing having a tension spring to reduce the amount of tension experienced by the spring.
In the above illustrated embodiment, the one-way bearings are each press-fitted in the central through hole of the body portion of the oil brake apparatus via the bearing mount. However, the present invention is not limited thereto, and the one-way bearing may be press-fitted directly into the central through hole of the body portion of the oil brake apparatus.
In the above-shown embodiments, in order to clearly illustrate the inventive concept, the one-way bearing in the oil brake apparatus takes the form of a needle bearing. The present invention is not limited thereto and the inventive concept of the present invention may also be applied to oil brake mechanisms having other forms of one-way bearings. For example, the oil brake apparatus of the present invention may also include a ball bearing.
In the above embodiments, the concept of the present invention has been described in connection with an oil brake device of a scroll compressor. It should be noted that the concepts of the present invention may be applied to other one-way bearings to provide a one-way bearing assembly that reduces the amount of spring deflection to reduce the risk of spring wear and breakage and to any structure having a one-way bearing other than an oil-removing brake.
Herein, exemplary embodiments of the present invention have been described in detail, but it should be understood that the present invention is not limited to the specific embodiments described and illustrated in the above. Those skilled in the art will be able to make various modifications and variations to the invention without departing from the spirit and scope of the invention. All such modifications and variations are intended to be within the scope of the present invention. Moreover, all the components described herein may be replaced by other technically equivalent elements.
List of reference numerals
1. Air suction port 2 and air discharge port 3 movable vortex piece
4. Fixed scroll 5 rotary shaft 6 motor
S1 shell S2 base S3 top cover
S4 baffle OL lubricating oil
10. 20, 30 oil brake 11, 21, 31 body parts
12. 22, 32 oil brake wings 13, 23, 33 central through hole
14. 24, 34 one-way bearing 15, 25, 35 bearing mount
131. 231, 331 outer lane 132 kingpin
133. Spring ends of springs 133a, 133b
134. Wedge-shaped groove of retainer 135
26. 36 upper limit parts 27, 37 lower limit parts.
Claims (18)
1. A one-way bearing assembly adapted to be mounted to a rotating shaft, the one-way bearing assembly comprising:
an outer ring, the inner peripheral surface of which is provided with a plurality of wedge-shaped groove parts, each wedge-shaped groove part comprises a wide end and a narrow end;
an annular retainer disposed inside the outer race;
a plurality of rollers held in the cage; and
a plurality of springs retained on the cage and having ends in contact with the respective rollers to bias the rollers toward the narrow ends;
wherein when the one-way bearing assembly is mounted to the rotating shaft, the plurality of rollers are movable in the circumferential direction of the outer race in corresponding wedge-shaped grooves of the outer race between a first position at the wide end, at which the rotating shaft is rotatable relative to the outer race and the rollers, the spring experiencing a maximum amount of deformation, and the plurality of rollers having a maximum inscribed circle of diameter D1, and a second position at which the rollers are engaged between the outer race and the rotating shaft to enable synchronous rotation of the outer race with the rotating shaft, the spring experiencing a minimum amount of deformation, and the plurality of rollers having a minimum inscribed circle of diameter D2, wherein D2 is less than D1;
The rotating shaft moves the plurality of rollers from the second position toward the first position in the corresponding wedge-shaped groove portion of the outer race when the rotating shaft rotates in a first direction, moves the plurality of rollers toward the second position in the corresponding wedge-shaped groove portion of the outer race when the rotating shaft rotates in a second direction opposite to the first direction,
wherein the one-way bearing assembly further comprises at least one stop mounted concentric with the outer race, the at least one stop being designed such that a circumferential position of the plurality of rollers is limited between the first and second positions when the rotating shaft rotates in the first direction.
2. A one-way bearing assembly according to claim 1, wherein the at least one stop is mounted fixed relative to the outer race and the at least one stop has an inner diameter less than D1 and greater than D2.
3. A one-way bearing assembly according to claim 1, wherein the at least one stop is fixed to the rotating shaft, the outer diameter of the at least one stop being arranged such that the spacing s between the outer periphery of the at least one stop and the inner wall of the bearing mount fitted on the outer ring is less than half the difference between D1 and D2.
4. A one-way bearing assembly according to claim 1, wherein the at least one stop is designed such that a maximum radial displacement L of the plurality of rollers, when the rotating shaft rotates in the first direction, satisfies the following relationship with D1, D2:
L＝0.5×(D1-D2)×a，
wherein a is greater than 0 and less than 1.
5. The one-way bearing assembly of claim 4, wherein the at least one stop is mounted stationary relative to the outer race and a spacing distance between an inner peripheral surface of the at least one stop and an outer peripheral surface of the rotating shaft is equal to the maximum radial displacement L.
6. The one-way bearing assembly of claim 4, wherein the at least one stop is fixed to the rotating shaft such that when the radial displacement of the plurality of rollers reaches the maximum radial displacement L, the at least one stop is blocked such that the radial displacement of the plurality of rollers cannot be further increased.
7. The one-way bearing assembly of any one of claims 4-6, wherein a is a value between 0.01 and 0.2.
8. A one-way bearing assembly according to any one of claims 1-6, wherein the at least one stop is provided at a longitudinal end of the outer race.
9. A one-way bearing assembly according to claim 8, wherein the at least one stop is in contact with the longitudinal end of the outer race.
10. The one-way bearing assembly of any one of claims 1-6, wherein the at least one stop comprises a first stop mounted above a longitudinally upper end of the outer race and a second stop mounted below a longitudinally lower end of the outer race.
11. A one-way bearing assembly according to any one of claims 1-6, wherein the at least one stop is an aluminum ring.
12. An oil brake apparatus adapted to be mounted to a rotating shaft, the oil brake apparatus comprising:
a body portion having a central through hole; and
one or more oil brake wings extending radially outwardly from the body portion;
wherein the oil brake apparatus further comprises a one-way bearing assembly according to any one of claims 1-11, the one-way bearing assembly being located in the central through bore and the outer race being press fit in the central through bore.
13. The oil brake apparatus of claim 12, wherein the one or more oil brake wings are integrally formed with the body portion.
14. An oil brake apparatus according to claim 12, wherein the outer race is press fit in the central through bore via a bearing mount.
15. An oil brake apparatus according to claim 14, wherein the at least one stop member is press fit within the bearing mount.
16. A scroll compressor characterized by comprising an oil brake apparatus according to any one of claims 12-15.
17. A scroll compressor, comprising:
a compression mechanism for compressing a working fluid, the compression mechanism including a fixed scroll and an orbiting scroll;
a rotation shaft that drives the movable scroll;
a motor that drives the rotation shaft to rotate in a first direction; and
an oil brake device mounted on the rotating shaft, and comprising:
a body portion having a central through hole; and
one or more oil brake wings extending radially outwardly from the body portion;
Wherein, oil brake equipment still includes one-way bearing, one-way bearing pressure-bearing fit is in the central through hole, one-way bearing includes:
an outer ring, the inner peripheral surface of which is provided with a plurality of wedge-shaped groove parts, each wedge-shaped groove part comprises a wide end and a narrow end;
an annular retainer disposed inside the outer race;
a plurality of rollers held in the cage; and
a plurality of springs retained on the cage and having ends in contact with the respective rollers to bias the rollers toward the narrow ends;
wherein the plurality of rollers are movable in the corresponding dovetail groove of the outer race between a first position at the wide end at which the rotational axis is rotatable relative to the outer race and the rollers, the spring experiencing a maximum amount of deformation, and the plurality of rollers having a maximum inscribed circle of diameter D1, and a second position at which the rollers are engaged between the outer race and the rotational axis to enable synchronous rotation of the outer race with the rotational axis, the spring experiencing a minimum amount of deformation, and the plurality of rollers having a minimum inscribed circle of diameter D2, wherein D2 is less than D1;
The rotating shaft moves the plurality of rollers from the second position toward the first position in the corresponding wedge-shaped groove portion of the outer race when the rotating shaft rotates in the first direction, moves the plurality of rollers toward the second position in the corresponding wedge-shaped groove portion of the outer race when the rotating shaft rotates in a second direction opposite to the first direction,
wherein the oil brake apparatus further comprises at least one stop fixed to the rotating shaft and located in the central through hole, the at least one stop being designed such that circumferential positions of the plurality of rollers are limited between the first and second positions when the rotating shaft rotates in the first direction.
18. The scroll compressor of claim 17, wherein the one-way bearing is press fit in the central throughbore via a bearing mount.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710847868.9A CN109519372B (en) | 2017-09-19 | 2017-09-19 | One-way bearing assembly, oil brake device and scroll compressor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710847868.9A CN109519372B (en) | 2017-09-19 | 2017-09-19 | One-way bearing assembly, oil brake device and scroll compressor |
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| CN109519372A CN109519372A (en) | 2019-03-26 |
| CN109519372B true CN109519372B (en) | 2024-01-23 |
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