JP4142383B2 - Full system rotary scroll compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a full-system rotary scroll compressor suitably used for compressing a gas such as air or a refrigerant, for example.
[0002]
[Prior art]
In general, the whole-system rotary scroll compressor includes a cylindrical casing that extends in the axial direction, a drive scroll that is rotatably provided in the casing and is driven to rotate by a rotation source, and is opposed to the drive scroll. A driven scroll that is rotatably provided in the casing and forms a plurality of compression chambers between the driven scroll and the driven scroll, and is provided between the driven scroll and the driven scroll so as to continuously reduce the compression chambers. There is known an auxiliary crank mechanism that rotates the driven scroll relative to the driving scroll (see, for example, Patent Document 1 and Patent Document 2).
[0003]
[Patent Document 1]
Japanese Patent Laid-Open No. 3-145588
[Patent Document 2]
JP-A-9-133307
[0004]
In this type of conventional rotary scroll compressor according to the prior art, when the drive scroll is rotationally driven by a rotation source such as an electric motor, this rotation is transmitted to the driven scroll via the auxiliary crank mechanism, and at this time the driven scroll is driven. And the driving scroll perform a relative orbiting motion with a constant eccentric dimension, thereby continuously reducing the compression chamber between the two scrolls, and sequentially compressing a fluid such as air in each compression chamber.
[0005]
In addition, the auxiliary crank mechanism used in such a conventional full-system rotary scroll compressor has a shaft insertion hole provided in each of the drive scroll and the driven scroll, and both sides in the axial direction are in the respective shaft insertion holes. Each of the crankshafts inserted therein, and bearings provided between both sides of the crankshaft in the axial direction and the respective shaft insertion holes and rotatably supporting the crankshafts in the respective shaft insertion holes, Each bearing is supplied with lubricating oil such as grease.
[0006]
[Problems to be solved by the invention]
By the way, the whole-system rotary scroll compressor according to the above-described prior art is configured such that when the driving scroll is driven to rotate, the driven scroll is also rotated, so that the auxiliary crank provided between the two scrolls is also provided. The centrifugal force accompanying the rotation of each scroll continues to act on the bearing of the mechanism.
[0007]
For this reason, lubricant such as grease supplied to the bearing of the auxiliary crank mechanism has a strong tendency to leak from the inside of the bearing due to the action of centrifugal force, and it is difficult to keep the bearing of the auxiliary crank mechanism in a lubricated state for a long time. There's a problem.
[0008]
The present invention has been made in view of the above-mentioned problems of the prior art, and an object of the present invention is to prevent a lubricant such as grease from leaking from the bearing and to keep the bearing of the auxiliary crank mechanism in a lubricated state for a long time. Another object of the present invention is to provide a full-system rotary scroll compressor that can improve durability, service life, and the like.
[0009]
[Means for Solving the Problems]
In order to solve the above-described problems, the present invention provides a cylindrical casing that extends in the axial direction, a drive scroll that is rotatably provided in the casing and is driven to rotate by a rotation source, and is opposed to the drive scroll. A driven scroll that is rotatably provided in the casing and forms a plurality of compression chambers with the driving scroll, and is provided between the driven scroll and the driving scroll so as to continuously reduce the compression chambers. And an auxiliary crank mechanism for rotating the driven scroll relative to the drive scroll.
[0010]
The feature of the configuration adopted by the invention of claim 1 is that the auxiliary crank mechanism includes a shaft insertion hole provided in each of the drive scroll and the driven scroll, and both sides in the axial direction in the respective shaft insertion holes. A crankshaft to be inserted, a bearing provided between both sides of the crankshaft in the axial direction and the respective shaft insertion holes to rotatably support the crankshaft in the respective shaft insertion holes, and the respective bearings. A ring-shaped cover that prevents the lubricant for maintaining a lubrication state from leaking to the outside from the shaft insertion hole, and the ring-shaped cover is fixed by press-fitting the outer peripheral side into the shaft insertion hole; The inner peripheral side is attached to the crankshaft by clearance fitting.
[0011]
With this configuration, the outer peripheral side of the ring-shaped cover is press-fitted and fixed in the shaft insertion hole, so that the lubricant supplied to the bearing is applied to the outer ring side of the bearing and the outer peripheral side of the ring-shaped cover by the action of centrifugal force. Even in the state of being shifted to one side, the lubricant at this time can be prevented from leaking to the outside from between the outer peripheral side of the ring-shaped cover and the shaft insertion hole. Further, since the inner peripheral side of the ring-shaped cover is attached to the crankshaft with a clearance fit, the crankshaft can be smoothly rotated with respect to the ring-shaped cover.
[0012]
According to the invention of claim 2, a lubricant holding space having a volume larger than the amount of lubricant necessary to keep the bearing in a lubrication state is formed between the ring-shaped cover and the bearing. It is set as the structure which becomes.
[0013]
As a result, even when the lubricant supplied to the bearing is shifted to the outer ring side of the bearing and the outer periphery side of the ring-shaped cover by the action of centrifugal force, the lubricant is retained in the lubricant holding space having a large volume with a margin. Can continue.
[0014]
According to a third aspect of the present invention, the ring-shaped cover includes an outer diameter ring portion on the outer peripheral side, an inner diameter ring portion on the inner peripheral side, and a gap between the inner diameter ring portion and the outer diameter ring portion. A ring having a U-shaped cross-section with an annular connecting portion connected on the side, and a lubricant holding space is formed between a tangent line of the inner diameter ring portion and the outer diameter ring portion positioned radially outward of the tangential line. The volume of the formed arcuate space is configured to be greater than the amount of lubricant required for the bearing.
[0015]
As a result, even when the lubricant supplied to the bearing is shifted to the outer ring side of the bearing and the outer periphery side of the ring-shaped cover by the action of centrifugal force, the lubricant at this time is put into the arc-shaped space portion of the lubricant holding space. Thus, the lubricant in the lubricant holding space can be prevented from leaking outside through a small gap formed between the inner ring portion of the ring-shaped cover and the crankshaft.
[0016]
Further, according to the invention of claim 4, the ring-shaped cover is formed using a material having a thermal expansion coefficient equal to or higher than that of the material of the driving scroll and the driven scroll. As a result, even if the driving scroll and the driven scroll are thermally expanded due to heat generated by the compression operation, the ring-shaped cover is thermally expanded to be equal to or more than the two scrolls, so an extra gap is formed between the ring-shaped cover and the shaft insertion hole. Is not formed, and leakage of the lubricant can be continuously prevented.
[0017]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a case where the entire system rotary scroll compressor according to the embodiment of the present invention is used as an air compressor will be described as an example and described in detail with reference to the accompanying drawings.
[0018]
Here, FIG. 1 to FIG. 3 show a first embodiment of the present invention. In the figure, reference numeral 1 denotes a cylindrical casing constituting the outer frame of the scroll compressor. The casing 1 includes a casing main body 2 formed in a substantially cylindrical shape with an axis O1-O1 or an axis O2-O2 as a center, The casing body 2 is composed of left and right shaft supports 3, 4 and the like which are fixed to the left and right ends of the casing body 2, respectively.
[0019]
In this case, the casing body 2 of the casing 1 can be divided into two case bodies 2A and 2B at the middle in the axial direction as shown in FIG. The case bodies 2A and 2B are integrated with each other by using bolts or the like as shown in FIG. 1 after assembling a drive scroll 14 and a driven scroll 20 which will be described later.
[0020]
An annular lid 5 is provided on the other axial side of the casing main body 2 at a position facing the shaft support 4 in the axial direction. The lid 5 includes a driven shaft 17 (described later) on the shaft support 4. It is supported so that it can rotate between. The lid 5 is attached with a sealing flange 35, which will be described later, on the outer end face thereof.
[0021]
6 is an electric motor as a rotation source provided on one side of the casing body 2 on the shaft support 3 side. The electric motor 6 is a cylindrical motor fixed to the end of the casing body 2 and extending in the axial direction. Case 7, lid body 8 with the end of motor case 7 closed, cylindrical stator 9 provided on the inner peripheral side of motor case 7, and rotatably disposed on the inner peripheral side of stator 9 It is comprised by the cylindrical rotor 10 made.
[0022]
In the electric motor 6, the axes of the stator 9 and the rotor 10 are arranged on the same axis as the axis O1-O1 of the drive shaft 11 to be described later. By rotating the rotor 10, the drive shaft 11 is moved along the axis O1-O1. It is rotationally driven as the center.
[0023]
Reference numeral 11 denotes a drive shaft as a rotary shaft rotatably provided on the lid body 8 and the shaft support 3 of the electric motor 6, and the drive shaft 11 uses means such as press fitting into the rotor 10 of the electric motor 6. The shaft 10 is a solid shaft body fitted together and rotates integrally with the rotor 10 about the axis O1-O1.
[0024]
The drive shaft 11 is supported on one side in the axial direction (left end side in FIG. 1) via the bearing 12 on the lid body 8 of the electric motor 6, and the other side in the axial direction is supported by the shaft support 3 on the other side. The bearings 13 and 13 are rotatably supported. In this case, the bearing 13 is configured using an angular ball bearing or the like that can receive a radial load and a thrust load.
[0025]
A drive scroll 14 is rotatably provided in the casing body 2 via the drive shaft 11, and the drive scroll 14 is fixed to the end of the drive shaft 11 as shown in FIG. 1. It comprises a body 15 and a scroll member 16 (described later) that is attached to the drive rotator 15 in a retaining state and rotates integrally with the drive rotator 15. And the drive rotary body 15 is formed using metal materials, such as aluminum, for example.
[0026]
Reference numeral 16 denotes a drive-side scroll member, which is formed in a substantially disc shape as shown in FIG. 1 and is disposed in the drive rotator 15 so that its center coincides with the axis O1-O1 of the drive shaft 11. The end plate 16A is formed, and a spiral wrap portion 16B standing on the surface of the end plate 16A.
[0027]
When the driving rotary body 15 rotates about the axis O1-O1 as the driving shaft 11 rotates, the scroll member 16 rotates integrally with the driving rotary body 15 to drive the driven scroll. Each compression chamber 23 is continuously reduced between the members 22.
[0028]
Reference numeral 17 denotes a driven shaft as another rotating shaft rotatably provided on the shaft support body 4 and the lid body 5 on the other side of the casing body 2, and the driven shaft 17 has an axial hole 17A extending in the axial direction. It is formed as a hollow shaft body, and is arranged on an axis O2-O2 that is eccentric with respect to the axis O1-O1 of the drive shaft 11 by a dimension δ.
[0029]
The driven shaft 17 is supported on one side in the axial direction rotatably on the shaft support 4 via bearings 18, 18, and the other side in the axial direction is supported on the lid 5 via another bearing 19. Yes. Each bearing 18 on the driven shaft 17 side is configured by using an angular ball bearing or the like that can receive a radial load and a thrust load.
[0030]
In this case, the bearing 13 on the drive shaft 11 side and the bearing 18 on the driven shaft 17 side are mounted with their assembly directions reversed as shown in FIG. 1, and compressed air generated in a compression chamber 23 described later. Even when the drive shaft 11 and the driven shaft 17 receive thrust loads in opposite directions at a pressure such as, the thrust load is received via the shaft supports 3 and 4 and the axial direction between the scroll members 16 and 22 is received. The gap is kept almost constant.
[0031]
Reference numeral 20 denotes a driven scroll which is axially opposed to the driving scroll 14 and is rotatably provided in the casing body 2. The driven scroll 20 is fixed to the end of the driven shaft 17 as shown in FIG. The driven rotator 21 and a scroll member 22 which is attached to the driven rotator 21 in a retaining state and rotates together with the driven rotator 21 are described below. The driven rotator 21 is formed using the same material as the drive rotator 15 (for example, aluminum).
[0032]
A scroll member 22 on the driven side is formed in a substantially disc shape as shown in FIG. 1, and is arranged in the driven rotating body 21 so that the center thereof coincides with the axis O2-O2 of the driven shaft 17. The end plate 22A is formed, and a spiral wrap portion 22B standing on the surface of the end plate 22A.
[0033]
Here, the driven scroll 20 is arranged such that the lap portion 22B of the scroll member 22 overlaps the lap portion 16B on the drive scroll 14 side with a predetermined angle (for example, 180 °) and overlaps. A plurality of compression chambers 23, 23,... Are formed between the outer peripheral side and the inner peripheral side.
[0034]
The driven scroll 20 is provided with a discharge hole 24 located on the center side of the end plate 22 </ b> A, and the discharge hole 24 communicates with the shaft hole 17 </ b> A of the driven shaft 17. Further, on the outer peripheral side of the driven scroll 20, a suction port (not shown) for sucking air (outside air) into the compression chamber 23 on the outermost peripheral side among the compression chambers 23 is provided.
[0035]
The drive scroll 14 and the driven scroll 20 are rotated relative to each other via an auxiliary crank mechanism 25 described later, thereby continuously reducing the compression chambers 23 therebetween, and the outermost compression chambers from the suction port. The high-pressure compressed air is discharged from the discharge hole 24 into the shaft hole 17 </ b> A of the driven shaft 17 while guiding the air sucked into the pressure chamber 23 toward the compression chamber 23 on the inner peripheral side so as to gradually increase the pressure. .
[0036]
25, 25,... Are a plurality of auxiliary crank mechanisms provided between the driving scroll 14 and the driven scroll 20, and each auxiliary crank mechanism 25 is arranged in the circumferential direction of the driving rotary body 15 and the driven rotary body 21, for example. A total of three are arranged at intervals of about 120 °. The auxiliary crank mechanism 25 transmits rotation between the driving scroll 14 and the driven scroll 20 and generates a relative turning motion between the driving scroll 14 and the driven scroll 20.
[0037]
As shown in FIG. 2, the auxiliary crank mechanism 25 includes stepped holes 26 and 27 as shaft insertion holes formed on the outer peripheral sides of the drive rotator 15 and the driven rotator 21, respectively, and bearings 28 and 27 described later. 29, a crankshaft 30, ring-shaped covers 31, 32, and the like.
[0038]
In this case, the stepped hole 26 of the drive rotor 15 is composed of a circular large-diameter hole portion 26A, a medium-diameter hole portion 26B, and a small-diameter hole portion 26C centered on the axis O3-O3 as shown in FIG. An annular groove 26D capable of accommodating a grease G described later is formed at the step between the diameter hole 26A and the medium diameter hole 26B.
[0039]
The stepped hole 27 of the driven rotor 21 is composed of a circular large-diameter hole portion 27A, a medium-diameter hole portion 27B, and a small-diameter hole portion 27C centered on the axis O4-O4. An annular groove 27 </ b> D capable of accommodating the grease G is formed in the step between the diameter hole 27 </ b> B.
[0040]
The axis O3 -O3 of the stepped hole 26 and the axis O4 -O4 of the stepped hole 27 are eccentric from each other by the dimension δ, like the axis O1 -O1 of the drive shaft 11 and the axis O2 -O2 of the driven shaft 17. Is. In the stepped holes 26 and 27, the large-diameter holes 26A and 27A are formed to have substantially the same hole diameter, and the medium-diameter holes 26B and 27B are also formed to have substantially the same hole diameter.
[0041]
Reference numeral 28 denotes a drive-side bearing mounted in the stepped hole 26 of the drive rotor 15, and the bearing 28 is formed of, for example, a ball bearing as shown in FIG. The outer ring 28A fitted to the inner ring 28B, the inner ring 28B fitted to the outer peripheral side of the shaft portion 30A, which will be described later, and a plurality of rolling elements arranged so as to be able to roll between the inner ring 28B and the outer ring 28A. It is comprised by the spherical body 28C.
[0042]
Reference numeral 29 denotes a driven-side bearing mounted in the stepped hole 27 of the driven rotor 21, and the bearing 29 is composed of a ball bearing substantially the same as the drive-side bearing 28, and has a large-diameter hole portion of the stepped hole 27. 27A, an outer ring 29A fitted into the inner ring 29B, an inner ring 29B fitted to the outer peripheral side of a shaft portion 30B, which will be described later, and a plurality of rolling elements arranged so as to be able to roll between the inner ring 29B and the outer ring 29A. And a sphere 29C.
[0043]
Here, these bearings 28 and 29 are maintained in a lubrication state by supplying a lubricant such as grease G, for example. The amount of lubricant (grease G) necessary to keep the bearings 28 and 29 in a lubrication state is, for example, the dynamic space volume of the rolling element previously proposed in Japanese Patent No. 2950438 (for example, a bearing). It is preferable to set it in a range of 40 to 60% with respect to the dynamic space volume of each spherical body 28C between the 28 outer rings 28A and 28B.
[0044]
Reference numeral 30 denotes a crankshaft mounted in the stepped holes 26 and 27 via bearings 28 and 29. The crankshaft 30 includes a shaft portion 30A on one side in the axial direction and the other side in the axial direction as shown in FIG. The shaft portion 30B, a large-diameter annular plate portion 30C positioned between the shaft portions 30A and 30B, and a flange portion 30D formed integrally between the annular plate portion 30C and the shaft portion 30A. The other flange portion 30E is integrally formed between the annular plate portion 30C and the shaft portion 30B.
[0045]
In the crankshaft 30, the shaft portion 30A, the annular plate portion 30C and the flange portion 30D on one side have a circular shape centered on the axis O3-O3, and the shaft portion 30B and the flange portion 30E on the other side have an axis O4. It is formed as a circular body centered on -O4. Further, the shaft portions 30A and 30B of the crankshaft 30 are formed with substantially the same outer diameter, and the flange portions 30D and 30E are also formed with substantially the same outer diameter.
[0046]
Here, the shaft portion 30A of the crankshaft 30 is rotatably mounted in the stepped hole 26 of the drive rotator 15 via the bearing 28, and the other side shaft portion 30B is a stepped hole of the driven rotator 21. 27 is rotatably mounted in a bearing 27 through a bearing 29. Then, the flange portions 30D and 30E of the crankshaft 30 make contact with the inner rings 28B and 29B of the bearings 28 and 29 to prevent the bearings 28 and 29 from being removed in the stepped holes 26 and 27.
[0047]
Reference numerals 31 and 32 denote ring-shaped covers that are fitted into the stepped holes 26 and 27. The ring-shaped covers 31 and 32 are made of a material such as aluminum and have a U-shaped cross section as shown in FIG. It is formed as a ring having a shape, and its thermal expansion coefficient is equal to that of the drive rotator 15 and the driven rotator 21.
[0048]
As shown in FIGS. 2 and 3, the ring-shaped cover 31 includes an outer diameter ring portion 31A on the outer peripheral side, an inner diameter ring portion 31B on the inner peripheral side, an inner diameter ring portion 31B and an outer diameter ring portion 31A. It is comprised by the cyclic | annular connection part 31C which connects between them integrally by the one side of an axial direction. Similarly to the ring-shaped cover 31, the ring-shaped cover 32 includes an outer diameter ring portion 32A, an inner diameter ring portion 32B, and an annular coupling portion 32C.
[0049]
The ring-shaped covers 31 and 32 are fitted into the stepped holes 26 and 27 of the drive rotator 15 and the driven rotator 21 as shown in FIG. 2, and at this time, the outer diameter ring portions 31A and 32A are large. It is press-fitted into the hole portions 26A and 27A and fixed. Further, the inner ring portions 31B and 32B are attached to the flange portions 30D and 30E of the crankshaft 30 by clearance fitting to compensate for the crankshaft 30 rotating smoothly with respect to the ring-shaped covers 31 and 32. Yes.
[0050]
33 and 34 are lubricant holding spaces formed between the ring-shaped covers 31 and 32 and the bearings 28 and 29. The lubricant holding spaces 33 and 34 are annular grooves 26D and 26D of the stepped holes 26 and 27, respectively. Together with 27D, it is formed as an annular space having a volume sufficiently larger than the amount of grease G necessary to keep the bearings 28 and 29 in a lubricated state.
[0051]
In particular, the lubricant holding spaces 33 and 34 have, for example, arcuate space portions 33A and 34A indicated by hatching in FIG. 3 to have a volume equal to or greater than the necessary amount of grease G described above. Is formed.
[0052]
In this case, as illustrated in FIG. 3, the arcuate space portion 33A includes a virtual tangent line S that contacts the inner circumference of the inner diameter ring portion 31B at the position of the point P, and a radially outer side of the tangent line S of the outer diameter ring portion 31A. This refers to a space portion (a hatched portion in FIG. 3) formed in a bow shape with the inner peripheral wall of the outer diameter ring portion 31A located at the position. The same applies to the arcuate space portion 34A.
[0053]
As shown in FIG. 1, a sealing flange 35 is provided so as to abut against the lid 5, and the sealing flange 35 surrounds the end of the driven shaft 17 protruding from the lid 5 from the outside in the radial direction. As a result, the outer peripheral side of the protruding end of the driven shaft 17 is sealed from the outside, and the smooth rotation of the driven shaft 17 within the sealing flange 35 is compensated.
[0054]
Further, a discharge port 36 is formed in the sealing flange 35 on the axis O 2 -O 2, and the discharge port 36 is connected to the discharge hole 24 of the driven scroll 20 via the shaft hole 17 A of the driven shaft 17. Communicate. The discharge port 36 is connected to an external air tank (not shown) via a pipe or the like.
[0055]
The scroll compressor according to the present embodiment has the above-described configuration, and the operation thereof will be described next.
[0056]
First, when the rotor 10 is rotationally driven by supplying power to the stator 9 side of the electric motor 6, the drive shaft 11 integrated with the rotor 10 rotates together with the drive scroll 14 about the axis O1-O1. Then, the rotation of the drive scroll 14 is transmitted to the driven scroll 20 via a plurality of auxiliary crank mechanisms 25.
[0057]
The driven scroll 20 and the driven shaft 17 are arranged on an axis O2-O2 which is eccentric by a dimension δ with respect to the axis O1-O1, and the crankshaft 30 of the auxiliary crank mechanism 25 is also a shaft portion on the axis O3-O3. 30A and the shaft portion 30B on the axis O4 -O4 are eccentric by the dimension δ.
[0058]
For this reason, the driven scroll 20 performs a relative turning motion with a turning radius of a dimension δ with respect to the driving scroll 14 by transmitting the rotation of the driving scroll 14 through each auxiliary crank mechanism 25, The driven shaft 17 and the driven shaft 17 are driven to rotate about the axis O2-O2.
[0059]
As a result, the compression chambers 23, 23,... Formed between the driving scroll 14 and the driven scroll 20 are continuously reduced in accordance with the relative turning operation between the scrolls 14, 20, and are driven. The air is sequentially compressed in each compression chamber 23 while sucking outside air from a suction port (not shown) provided on the outer peripheral side of the scroll 20.
[0060]
Then, the compressed air compressed in each compression chamber 23 between the drive scroll 14 and the driven scroll 20 passes through the discharge hole 24 provided in the center of the driven scroll 20 to the shaft hole 17A of the driven shaft 17 and the sealing flange. It is discharged to the outside through the 35 discharge ports 36 and stored in, for example, an air tank (not shown).
[0061]
Further, the bearings 28 and 29 of the auxiliary crank mechanism 25 include, for example, a moving space volume of the rolling element previously proposed by the present applicant in Japanese Patent No. 2950438 (the spherical bodies 28C between the outer ring 28A and the inner ring 28B of the bearing 28). The volume (oil amount) of grease G that is 40 to 60% or more of the dynamic space volume) is supplied as a lubricant, and between the outer rings 28A, 29A, inner rings 28B, 29B and the respective spheres 28C, 29C. The grease G can be kept in a lubrication state.
[0062]
By the way, in the whole-system rotary scroll compressor, while the driving scroll 14 and the driven scroll 20 perform the relative turning motion, the axis O1 -O1 and the axis O2 -O2 shown in FIG. Since the drive scroll 14 and the driven scroll 20 are rotated at a high speed around the center, a centrifugal force corresponding to the rotation speed is generated, and this centrifugal force is supplied to the bearings 28 and 29 of the auxiliary crank mechanism 25. It also affects G.
[0063]
That is, the bearing 28 and the ring-shaped cover 31 provided in the stepped hole 26 of the drive rotator 15 are rotated in the direction indicated by the arrow B by the rotation of the drive rotator 15 (the rotation in the direction indicated by the arrow A illustrated in FIG. 3). Receive centrifugal force. For this reason, the grease G (lubricant) supplied to the bearing 28 is subjected to the action of centrifugal force in the lubricant holding space 33 of the ring-shaped cover 31, thereby causing the grease G (lubricant) in the direction indicated by arrow B along the outer diameter ring portion 31A. While being pushed up, for example, they are gathered together in an arcuate space portion 33A indicated by oblique lines in FIG.
[0064]
At this time, when the amount of the grease G supplied to the bearing 28 becomes larger than the volume of the arcuate space portion 33A, a part of the grease G starts from the vicinity of the point P shown in FIG. Overflowing to the side and passing through the clearance between the flange portion 30D of the crankshaft 30 and the inner diameter ring portion 31B of the ring-shaped cover 31 (the clearance between the annular plate portion 30C and the annular coupling portion 31C). It will leak from the step hole 26 to the outside.
[0065]
However, in the present embodiment, in order to prevent the grease G from leaking from the bearings 28 and 29 of the auxiliary crank mechanism 25, the ring-shaped covers 31 and 32 are stepped on the drive rotator 15 and the driven rotator 21. The outer diameter ring portions 31A and 32A are press-fitted and fixed in the large diameter hole portions 26A and 27A, and the inner diameter ring portions 31B and 32B are fixed to the crankshaft 30. It is set as the structure attached by clearance fitting with respect to the flange parts 30D and 30E.
[0066]
Then, the lubricant holding spaces 33 and 34 formed between the ring-shaped covers 31 and 32 of the auxiliary crank mechanism 25 and the bearings 28 and 29 are the arcuate space portions 33A and 34A illustrated by hatching in FIG. The volume is configured to be equal to or larger than the amount of grease G necessary to keep the bearings 28 and 29 in a lubricated state.
[0067]
Therefore, the bearings 28 and 29 are lubricated between the ring-shaped covers 31 and 32 of the auxiliary crank mechanism 25 and the bearings 28 and 29 in the arc-shaped space portions 33A and 34A of the lubricant holding spaces 33 and 34. The amount of grease G equal to or greater than the amount necessary for maintaining the bearings 28 and 29 can be ensured, and the bearings 28 and 29 can be maintained in a lubricated state by the grease G.
[0068]
Therefore, according to the present embodiment, providing the auxiliary crank mechanism 25 with the ring-shaped covers 31 and 32 can prevent the grease G from leaking from the bearings 28 and 29, and the bearings 28 and 29 of the auxiliary crank mechanism 25. Can be maintained in a lubrication state over a long period of time, and the durability, life and the like can be reliably improved, and the reliability of the entire rotary scroll compressor can be improved.
[0069]
Further, in this case, the ring-shaped covers 31 and 32 are formed using the same material (for example, aluminum) as that of the driven rotating body 15 of the driving scroll 14 and the driven rotating body 21 of the driven scroll 20. Even if the drive rotator 15 and the driven rotator 21 are thermally expanded due to heat generated by the operation, an extra gap is formed between the stepped holes 26 and 27 of the scrolls 14 and 20 and the ring-shaped covers 31 and 32. The leakage of the grease G can be prevented over a long period of time.
[0070]
Next, FIG. 4 shows a second embodiment of the present invention. The feature of this embodiment is that a ring-shaped cover and a bottomed cover are provided in the shaft insertion holes of the driving scroll and the driven scroll, and these covers. There exists in the structure arrange | positioned so that a bearing may be pinched | interposed between them. In the present embodiment, the same components as those in the first embodiment described above are denoted by the same reference numerals, and the description thereof is omitted.
[0071]
In the figure, reference numeral 41 denotes an auxiliary crank mechanism employed in the present embodiment. The auxiliary crank mechanism 41 has bearings 28 and 29 and a crankshaft 30 as in the auxiliary crank mechanism 25 described in the first embodiment. Both are constituted by stepped holes 42 and 43, bottomed covers 44 and 45, ring-shaped covers 46 and 47, and the like, which will be described later.
[0072]
Reference numerals 42 and 43 denote stepped holes as shaft insertion holes formed in the drive rotating body 15 and the driven rotating body 21, respectively. These stepped holes 42 and 43 are the stepped holes described in the first embodiment. In substantially the same manner as the holes 26 and 27, they are constituted by large-diameter holes 42A and 43A, medium-diameter holes 42B and 43B, and small-diameter holes 42C and 43C.
[0073]
However, in this case, the medium diameter holes 42B and 43B are larger in diameter than the large diameter holes 42A and 43A, that is, larger than the inner diameters of the outer rings 28A and 29A of the bearings 28 and 29, and larger than the outer diameters of the outer rings 28A and 29A. Is also formed with a small hole diameter. The stepped hole 42 of the drive rotator 15 is disposed on the axis O3 -O3, and the stepped hole 43 of the driven rotator 21 is disposed on the axis O4 -O4.
[0074]
Reference numerals 44 and 45 denote bottomed covers fitted in the middle diameter holes 42B and 43B of the stepped holes 42 and 43. The bottomed covers 44 and 45 are made of a material such as aluminum. It is formed in a bottom cylindrical shape, and its thermal expansion coefficient is equivalent to that of the drive rotator 15 and the driven rotator 21.
[0075]
The bottomed covers 44 and 45 are press-fitted into the medium-diameter hole portions 42B and 43B on the outer peripheral side, and the thick cylindrical portions 44A surrounding the shaft portions 30A and 30B of the crankshaft 30 with a gap from the outside on the inner peripheral side. 45A and thin bottom portions 44B and 45B in which ends of the cylindrical portions 44A and 45A are closed.
[0076]
The cylindrical portions 44A, 45A of the bottomed covers 44, 45 are provided with annular grooves 44C, 45C capable of accommodating the grease G on the contact surface side with the bearings 28, 29, and these annular grooves 44C. , 45C are formed in substantially the same manner as the annular grooves 26D, 27D described in the first embodiment.
[0077]
Reference numerals 46 and 47 denote ring-shaped covers that are fitted into the stepped holes 42 and 43. The ring-shaped covers 46 and 47 are the same as the ring-shaped covers 31 and 32 described in the first embodiment. The coefficient of thermal expansion is equal to the coefficient of thermal expansion of the drive rotator 15 and the driven rotator 21.
[0078]
The ring-shaped covers 46 and 47 are constituted by outer ring portions 46A and 47A, inner ring portions 46B and 47B, and annular coupling portions 46C and 47C, and bearings 28 and 29 in the stepped holes 42 and 43 (in particular, The outer rings 28A, 29A) are arranged so as to be sandwiched between the bottomed covers 44, 45 from both sides in the axial direction.
[0079]
Reference numerals 48 and 49 denote lubricant holding spaces formed between the ring-shaped covers 46 and 47 and the bearings 28 and 29. The lubricant holding spaces 48 and 49 are the lubricant holding spaces described in the first embodiment. It is configured in the same manner as the spaces 33 and 34, and is formed as an annular space having a volume sufficiently larger than the amount of grease G necessary to keep the bearings 28 and 29 in a lubricated state.
[0080]
Reference numerals 50 and 51 denote O-rings as sealing members provided between the large-diameter hole portions 42A and 43A of the stepped holes 42 and 43 and the bearings 28 and 29. These O-rings 50 and 51 are The outer rings 28A and 29A are elastically contacted from the outer peripheral side to seal between the outer rings 28A and 29A and the large-diameter holes 42A and 43A, and the bearings 28 and 29 are prevented from being removed from the outer rings 28A and 29A. It also has a function.
[0081]
Thus, in the present embodiment configured as described above, it is possible to obtain substantially the same operational effects as those of the first embodiment described above. In particular, in the present embodiment, the bottomed covers 44 and 45 are fitted and provided in the medium diameter holes 42B and 43B of the stepped holes 42 and 43, so that the large diameter holes 42A of the stepped holes 42 and 43 are provided. , 43A, the outer rings 28A, 29A of the bearings 28, 29 can be sandwiched between the bottomed covers 44, 45 and the ring-shaped covers 46, 47 from both sides in the axial direction, thereby preventing the leakage of the grease G more reliably. be able to.
[0082]
In the first embodiment, the ring-shaped covers 31 and 32 are formed using the same material (for example, aluminum) as that of the driven rotary body 15 of the driven scroll 14 and the driven rotary body 21 of the driven scroll 20. The case has been described as an example. However, the present invention is not limited to this. For example, the ring-shaped covers 31 and 32 may be formed of a material having a thermal expansion coefficient higher than that of the material of the drive rotator 15 and the driven rotator 21.
[0083]
As a result, even if the drive rotator 15 and the driven rotator 21 are thermally expanded due to heat generated by the compression operation, the ring-shaped covers 31 and 32 are thermally expanded beyond the both rotators 15 and 21. No extra gap is formed between the stepped holes 26 and 27, and leakage of a lubricant such as grease G can be continuously prevented. This is the same for the second embodiment.
[0084]
Further, in each of the embodiments, the case where the driving scroll 14 is configured by the driving rotating body 15 and the scroll member 16 and the driven scroll 20 is also configured by the driven rotating body 21 and the scroll member 22 has been described as an example. . However, the drive rotator 15 and the scroll member 16 (the driven rotator 21 and the scroll member 22) are not necessarily formed separately, and may be formed in advance as an integrated body.
[0085]
Furthermore, in each said embodiment, the scroll air compressor was mentioned as an example and demonstrated as a whole-system rotary scroll compressor. However, the present invention is not limited to this. For example, a gas other than air may be compressed, and the present invention may be applied to a refrigerant compressor or the like.
[0086]
【The invention's effect】
As described above in detail, according to the first aspect of the present invention, the auxiliary crank mechanism for rotating the driven scroll relative to the driven scroll has the shaft insertion hole provided in each of the driven scroll and the driven scroll, and the axial direction. The crankshaft is inserted between the respective shaft insertion holes, and the crankshaft is inserted between the respective shaft insertion holes. It is composed of a bearing to be supported and a ring-shaped cover that prevents the lubricant of each bearing from leaking to the outside from the shaft insertion hole, and this ring-shaped cover is fixed by press-fitting the outer peripheral side into the shaft insertion hole. Since the inner peripheral side is attached to the crankshaft with a clearance fit, the lubricant supplied to the bearing is shifted to the outer ring side of the bearing and the outer peripheral side of the ring-shaped cover by the action of centrifugal force. However, the lubricant at this time can be prevented from leaking to the outside from between the outer periphery of the ring-shaped cover and the shaft insertion hole, and the bearing of the auxiliary crank mechanism can be maintained in a lubricated state for a long period of time, and the durability and service life can be maintained. Etc. can be improved reliably.
[0087]
According to the second aspect of the present invention, the lubricant holding space having a volume larger than the amount of lubricant necessary to keep the bearing in a lubrication state between the ring-shaped cover and the bearing. The lubricant supplied to the bearing is lubricated in the lubricant holding space having a large volume even when the lubricant supplied to the bearing is biased to the outer ring side of the bearing and the outer peripheral side of the ring-shaped cover by the action of centrifugal force. The agent can be kept with a margin.
[0088]
According to a third aspect of the present invention, the ring-shaped cover is formed as a ring having a U-shaped cross section by an outer diameter ring portion, an inner diameter ring portion and an annular connecting portion, and the lubricant holding space is tangent to the inner diameter ring portion. And the volume of the arcuate space formed between the outer diameter ring portion located on the radially outer side of the tangent line is greater than the amount of lubricant required for the bearing, Even when the lubricant supplied to the bearing is biased to the outer ring side of the bearing and the outer periphery of the ring-shaped cover by the action of centrifugal force, the lubricant at this time continues to be held in the arcuate space of the lubricant holding space. It is possible to prevent the lubricant in the lubricant holding space from leaking outside through a small gap formed between the inner ring portion of the ring-shaped cover and the crankshaft.
[0089]
Further, according to the invention described in claim 4, since the ring-shaped cover is formed using a material having a thermal expansion coefficient equal to or higher than that of the driving scroll and the driven scroll, heat generated by the compression operation is generated. Even if the driving scroll and the driven scroll are thermally expanded, the ring-shaped cover will be thermally expanded to the same extent or more than both scrolls, and an extra gap is formed between the ring-shaped cover and the shaft insertion hole. Can be prevented, and leakage of the lubricant can be continuously prevented.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing a scroll compressor according to a first embodiment of the present invention.
2 is an enlarged longitudinal sectional view showing an auxiliary crank mechanism in FIG. 1. FIG.
3 is an enlarged front view of a ring-shaped cover showing a relationship between the lubricant holding space in FIG. 2 and grease contained therein.
FIG. 4 is an enlarged longitudinal sectional view showing an auxiliary crank mechanism of a scroll compressor according to a second embodiment.
[Explanation of symbols]
1 casing
2 Casing body
3, 4 shaft support
6 Electric motor (rotation source)
9 Stator
10 Rotor
11 Drive shaft
14 Driven scroll
15 Driven rotating body
16, 22 Scroll member
17 Driven shaft
20 Followed scroll
21 Followed rotating body
23 Compression chamber
24 Discharge hole
25, 41 Auxiliary crank mechanism
26, 27, 42, 43 Stepped hole (shaft insertion hole)
28, 29 Bearing
30 crankshaft
31, 32, 46, 47 Ring-shaped cover
31A, 32A, 46A, 47A Outer ring part
31B, 32B, 46B, 47B Inner ring part
31C, 32C, 46C, 47C Annular connection
33, 34, 48, 49 Lubricant holding space
G Grease (lubricant)

Claims (4)

A cylindrical casing extending in the axial direction, a driving scroll rotatably provided in the casing and driven to rotate by a rotation source, and a driving scroll rotatably provided in the casing facing the driving scroll, A driven scroll that forms a plurality of compression chambers between the driven scroll and the driven scroll and the drive scroll, and the driven scroll is rotated relative to the drive scroll so as to continuously reduce the compression chambers. In the whole-system rotary scroll compressor equipped with an auxiliary crank mechanism,
The auxiliary crank mechanism includes a shaft insertion hole provided in each of the drive scroll and the driven scroll, a crank shaft in which both sides in the axial direction are respectively inserted into the respective shaft insertion holes, and both sides in the axial direction of the crank shaft. Bearings provided between the shaft insertion holes and rotatably supporting the crankshaft in the shaft insertion holes, and a lubricant for holding the bearings in a lubricated state is provided from the shaft insertion holes. Consists of a ring-shaped cover that prevents leakage to the outside,
The ring-shaped cover is configured to be configured such that the outer peripheral side is press-fitted and fixed into the shaft insertion hole, and the inner peripheral side is attached to the crankshaft by clearance fitting. The lubricant holding space having a volume larger than the amount of lubricant necessary to keep the bearing in a lubricated state is formed between the ring-shaped cover and the bearing. Full system rotary scroll compressor. The ring-shaped cover includes an outer diameter ring portion on the outer periphery side, an inner diameter ring portion on the inner periphery side, and an annular connection portion that connects the inner diameter ring portion and the outer diameter ring portion on one side in the axial direction. It is formed as a ring having a U-shaped cross section, and the lubricant holding space is an arcuate space portion formed between a tangent line of the inner diameter ring portion and the outer diameter ring portion located radially outside the tangent line. The whole-system rotary scroll compressor according to claim 2, wherein the volume is configured to be equal to or greater than the amount of lubricant required for the bearing. 4. The entire system rotary scroll compression according to claim 1, wherein the ring-shaped cover is formed using a material having a thermal expansion coefficient equal to or higher than that of the material of the driving scroll and the driven scroll. Machine.

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