WO2021117137A1

WO2021117137A1 - Scroll compressor

Info

Publication number: WO2021117137A1
Application number: PCT/JP2019/048309
Authority: WO
Inventors: 小山田　具永; 近野　雅嗣; 柳瀬　裕一; 遼太飯島
Original assignee: 日立ジョンソンコントロールズ空調株式会社
Priority date: 2019-12-10
Filing date: 2019-12-10
Publication date: 2021-06-17
Also published as: JP7263553B2; JPWO2021117137A1

Abstract

This scroll compressor is provided with a closed container, a frame, a stationary scroll, an orbiting scroll, and a crankshaft. The invention is also provided with: a rotating shaft provided so as to protrude out to an anti-lap side of the orbiting scroll; an eccentric hole which is provided to an end section of the crankshaft and into which the rotating shaft is inserted; a slewing bearing provided between the rotating shaft and the eccentric hole; a main bearing that is provided between the crankshaft and the frame and substantially at the same position in the axial direction as the slewing bearing; a shaft thrust plate provided to the end part of the crankshaft; a thrust bearing that is provided to the frame and slides with the shaft thrust plate to support a thrust force acting on the crankshaft; and an oil groove provided to a surface that slides with the thrust bearing in the shaft thrust plate. The oil groove is formed in the radial direction at a location within 180° forward in the rotating direction of the crankshaft from a 0° location, where 0° is the direction of the eccentric hole in the crankshaft.

Description

Scroll compressor

The present invention relates to a scroll compressor that handles HFC-based refrigerants, natural refrigerants such as air, carbon dioxide, and other compressible gases, and in particular, is mainly provided on a plain bearing and a frame provided on the back surface of a swivel scroll. The present invention relates to a scroll compressor that uses a plain bearing as a bearing.

In order to improve the performance of air conditioners and save energy, scroll compressors are required to have a wide range of variable discharge capacity. In order to make the discharge capacity variable over a wide range, it is effective to expand the operating speed range of the scroll compressor. In particular, by increasing the maximum operating speed, it is possible to increase the maximum discharge capacity without enlarging the dimensions of the compressor. This makes it possible to realize a compact and high-capacity scroll compressor.

In order to increase the maximum operating speed of the scroll compressor, a double slide that can shorten the axial distance between the swivel bearing that supports the swivel motion of the swivel scroll and the main bearing that supports the crankshaft that transmits the rotation of the motor. A bearing (double slide bearing) structure is effective. By adopting this double slide bearing structure, the load acting on the main bearing can be reduced and the deformation of the crankshaft can be reduced, so that the reliability of the slide bearing can be improved.

As a conventional scroll compressor having this double slide bearing structure, for example, there is one described in Japanese Patent Application Laid-Open No. 59-141784 (Patent Document 1). In the scroll compressor described in Patent Document 1, two upper and lower thrust bearings that support a swing scroll (swivel scroll) are provided, and the upper bearing thereof is provided so as to coincide with the center of the swing scroll. It is stated that the lower bearing is provided so as to coincide with the center of rotation of the crankshaft.

It is also described that the two upper and lower thrust bearings described above support the thrust force via a brim portion provided integrally with the crankshaft or via an annular body provided separately from the crankshaft. Has been done.

Japanese Unexamined Patent Publication No. 59-141784

In the scroll compressor of Patent Document 1 described above, from the top, the swivel scroll, the upper thrust bearing, the brim portion (or annular body) of the crankshaft, the lower thrust bearing, and the sliding surface of the frame (bearing support) are in this order. It is arranged in the vertical direction and supports the swivel scroll and the crankshaft in the vertical direction while sliding each interface.

In a scroll compressor, the crankshaft flexes and deforms due to the centrifugal force acting on the swivel scroll, the gas load, the centrifugal force acting on the balance weight, and the like. In particular, the centrifugal force increases in proportion to the square of the speed, so when the speed is increased, the deformation of the crankshaft also increases accordingly. In addition to this bending deformation of the crankshaft, the bearing surface of the thrust bearing and the sliding surface on the crankshaft side that slides on it are completely separated due to gaps and misalignment of the bearings (main bearings, etc.) that support the rotation of the crankshaft. It is difficult to maintain parallelism, and both slide in an inclined, so-called one-sided contact state. When sliding in a one-sided contact state, it becomes difficult for an oil film to be formed on the sliding surface of the thrust bearing, and solid contact is likely to occur locally in the inclined direction, so that there is a problem that wear is likely to proceed.

An object of the present invention is to obtain a scroll compressor that can reduce wear even if the sliding interface of a thrust bearing that supports the crankshaft in the vertical direction becomes one-sided due to deformation or inclination of the crankshaft. ..

Another object of the present invention is to obtain a scroll compressor capable of reducing the manufacturing cost, adjusting the oil groove position, and appropriately maintaining the bearing gap of the main bearing.

In order to achieve the above object, the first feature of the present invention is a closed container, a frame fixed to the closed container, and a swirl provided in the closed container and erected on the end plate and the end plate. A fixed scroll having a shaped wrap, a swivel scroll having an end plate and a spiral wrap standing on the end plate, and meshing with the fixed scroll to form a compression chamber, and a crank that swivels the swivel scroll. A scroll compressor including a shaft, the swivel shaft provided so as to project on the opposite side of the swivel scroll, an eccentric hole provided at the end of the crankshaft into which the swivel shaft is inserted, and the swivel shaft. A thrust bearing provided between the eccentric hole and the main bearing provided between the crankshaft and the frame and at substantially the same position as the thrust bearing in the axial direction, and an end portion of the crankshaft. The shaft thrust plate provided on the frame, the thrust bearing provided on the frame and sliding with the shaft thrust plate to support the thrust force acting on the crankshaft, and the thrust bearing on the shaft thrust plate. The oil groove is provided with an oil groove provided on the surface, and the oil groove is located within 180 ° forward in the rotation direction of the crankshaft from the 0 ° position when the direction of the eccentric hole in the crankshaft is 0 °. It is formed in the radial direction.

A second feature of the present invention is a closed container, a frame fixed to the closed container, and a fixed scroll provided in the closed container and having an end plate and a spiral wrap standing on the end plate. A scroll compressor having an end plate and a spiral wrap erected on the end plate, a swivel scroll that meshes with the fixed scroll to form a compression chamber, and a crankshaft that swivels the swivel scroll. Between the swivel shaft provided on the opposite side of the swivel scroll, the eccentric hole provided at the end of the crankshaft into which the swivel shaft is fitted, and the swivel shaft and the eccentric hole. A main bearing provided between the crankshaft and the frame and at substantially the same position in the axial direction as the swivel bearing, and a shaft thrust plate provided at the end of the crankshaft. A thrust bearing provided on the frame to support the thrust force acting on the crankshaft by sliding with the shaft thrust plate, and an oil groove provided on the surface of the shaft thrust plate sliding with the thrust bearing. The shaft thrust plate is formed separately from the crankshaft and is fixed to the end of the crankshaft, and the end of the crankshaft is on the swivel scroll side of the eccentric hole. Is provided with a hole for fitting the shaft thrust plate, and has a convex portion that fits with the inner peripheral surface of the hole portion of the crankshaft on the inner diameter side of the shaft thrust plate, and the position of the convex portion and the above. The position of the main bearing is configured to be a position that does not overlap in the axial direction of the crankshaft.

According to the present invention having the first feature, wear can be reduced even if the sliding interface of the thrust bearing that supports the crankshaft in the vertical direction becomes one-sided due to deformation or inclination of the crankshaft. It has the effect of obtaining a compressor.

Further, according to the present invention having the second feature, it is possible to obtain an effect that a scroll compressor can be obtained in which the manufacturing cost can be reduced, the oil groove position can be adjusted, and the bearing gap of the main bearing can be appropriately maintained. Be done.

The vertical sectional view which shows Example 1 of the scroll compressor of this invention. FIG. 1 is an enlarged cross-sectional view of a main part near the top of the crankshaft shown in FIG. A perspective view of the shaft thrust plate shown in FIG. 2 as viewed from below. A perspective view of the upper part of the crankshaft shown in FIG. 1 as viewed from below. It is a figure which shows the modification 1 of the shaft thrust plate shown in FIG. 2 and corresponds to FIG. It is a figure which shows the modification 2 of the shaft thrust plate shown in FIG. 2, and corresponds to FIG. It is a figure which shows the modification 3 of the shaft thrust plate shown in FIG. 2, and is the perspective view which looked at the shaft thrust plate from above. It is a figure which shows the scroll compressor using the shaft thrust plate shown in FIG. 7, and is the figure corresponding to FIG. The vertical sectional view which shows Example 2 of the scroll compressor of this invention. FIG. 9 is an enlarged cross-sectional view of a main part near the top of the crankshaft shown in FIG.

Hereinafter, specific examples of the scroll compressor of the present invention will be described with reference to the drawings. In each figure, the parts with the same reference numerals indicate the same or corresponding parts.

Example 1 of the scroll compressor of the present invention will be described in detail with reference to FIGS. 1 to 4. FIG. 1 is a vertical sectional view showing Example 1 of the scroll compressor of the present invention, FIG. 2 is an enlarged sectional view of a main part near the top of the crankshaft shown in FIG. 1, and FIG. 3 is a downward view of the shaft thrust plate shown in FIG. FIG. 4 is a perspective view of the upper portion of the crankshaft shown in FIG. 1 as viewed from below.

First, the overall configuration of the scroll compressor of the first embodiment will be described with reference to FIG. The scroll compressor in this embodiment is a differential pressure lubrication system in which lubricating oil is supplied to the sliding portion by utilizing the pressure difference in the closed container.

The scroll compressor 1 is configured by housing the compression mechanism unit 2 and the drive unit 3 in a closed container 4. The compression mechanism unit 2 is composed of a fixed scroll 21, a swivel scroll 22, a frame 23 fixed to the closed container 4, an old dam joint 24 and the like that constitute a rotation prevention mechanism of the swivel scroll 22.

The fixed scroll 21 has an end plate 21a and a spiral wrap (fixed wrap) 21b erected perpendicularly to the end plate 21a, and a discharge port 21c is formed at the center of the wrap 21b. It is fixed to the frame 23 by a plurality of bolts 25.

The swivel scroll 22 has an end plate 22a and a spiral wrap (swivel wrap) 22b that stands perpendicular to the end plate 22a, and is located at the center of the end plate 22a on the opposite side (rear side). A substantially cylindrical swirl shaft 22c is provided so as to project.

The compression chamber 26 is formed by engaging the fixed scroll 21 and the swivel scroll 22, and the swirl scroll 22 swivels to reduce the volume of the compression chamber 26 and perform a compression operation. In this compression operation, working fluid such as refrigerant gas is sucked into the compression chamber 26 from the suction port 5 along with the turning motion of the swirling scroll 22, and the sucked working fluid passes through the compression stroke and is discharged from the fixed scroll 21 at the discharge port 21c. Is discharged into the discharge space 6 in the closed container 4.

The working fluid discharged into the discharge space 6 then passes through flow paths (not shown) formed on the outer peripheral surface of the end plate 21a of the fixed scroll 21 and the outer peripheral surface of the frame 23, respectively, and the drive unit 3 Flows into the space 7 in which the fluid is arranged, and is further discharged from the closed container 4 to the refrigeration cycle or the like via the discharge pipe 8. With this configuration, the space inside the closed container 4 is maintained at a substantially discharge pressure.

The drive unit 3 for rotating the swivel scroll 22 is fixed to the center of the motor 31 including the stator 31a and the rotor 31b fixed to the closed container 4 and the rotor 31b and rotates integrally, and the swivel scroll 22 is rotated. It is composed of a crankshaft 32 and the like for driving the above.

A main bearing 27 that supports the end of the crankshaft 32 is provided on the inner peripheral surface of the frame 23. Further, an eccentric hole 32b into which the swivel shaft 22c of the swivel scroll 22 is inserted is provided at the end of the crankshaft 32, and a swivel bearing 28 is provided between the swivel shaft 22c and the eccentric hole 32b. It is provided. The scroll compressor 1 of this embodiment has a double slide bearing structure in which the main bearing 27 and the swing bearing 28 are provided at substantially the same positions in the axial direction. Approximately the same position in the axial direction means that 80% or more or all of the swivel bearing 28 is the same as the axial position of the main bearing 27.

Further, in this embodiment, the upper end side of the crankshaft 32 is configured as a large-diameter spindle portion 32a, and the spindle portion 32a is rotationally supported by the spindle bearing 27. Further, the lower end side of the crankshaft 32 is rotationally supported by the auxiliary bearing 9. The sub-bearing 9 is provided in the sub-bearing housing 10, and the sub-bearing housing 10 is fixed to the sub-frame 11 fixed to the closed container 4.

The main bearing 27 and the sub-bearing 9 that rotatably support the crankshaft 32 are on the compression mechanism portion 2 side and the oil sump portion 12 side provided on the bottom of the closed container 4 with respect to the motor 31. It is arranged in and respectively.

The eccentric hole 32b is formed in the spindle portion 32a and is open to the swivel scroll 22 side. The swivel shaft 22c of the swivel scroll 22 is inserted into the eccentric hole 32b via the swivel bearing 28.

When the crankshaft 32 rotates, the eccentric hole 32b swivels, and the swivel scroll 22 swivels without rotating due to the action of the oldham joint 24. The swivel shaft 22c is axially movable and rotatably engaged with the eccentric hole 32b.

The oldham joint 24 is arranged in a back pressure chamber 29 formed by the swivel scroll 22 and the frame 23, and engages with the swivel scroll 22 and the key groove provided in the frame 23 to rotate the swivel scroll 22. It plays the role of a prevention mechanism. That is, the Oldham joint 24 is provided with two sets of orthogonal keys, one set slides on the key groove formed on the frame 23, and the remaining one set provides the key groove formed on the back surface of the swivel scroll 22. It is configured to slide.

An oil supply pipe 32c is provided at the lower end of the crankshaft 32 so that the oil in the oil sump portion 12 is pumped up by a differential pressure and supplied to the oil supply passage 32d formed at the center of the crankshaft 32. ..

Next, the configuration of the vicinity of the top of the crankshaft 32 (near the main shaft portion 32a) in the scroll compressor of the first embodiment will be described in detail with reference to FIG. FIG. 2 is an enlarged cross-sectional view of a main part near the top of the crankshaft shown in FIG.

As shown in FIG. 2, the main shaft portion 32a of the crankshaft 32 is rotatably supported and slid by a main bearing 27 provided on the inner peripheral side of the frame 23. An eccentric hole 32b that opens to the upper part is formed on the inner peripheral side of the spindle portion 32a at a position eccentric with respect to the center of the spindle portion 32a (the center of the crankshaft 32), and the eccentric hole 32b is swiveled. A swivel shaft 22c of the scroll 22 and a swivel bearing 28 fixed to the swivel shaft 22c are inserted. Therefore, by sliding the swivel bearing 28 with respect to the eccentric hole 32b, the swivel shaft 22c is rotatably engaged with the eccentric hole 32b. As a result, the swivel scroll 22 is configured to swivel as the crankshaft 32 rotates.

In this embodiment, a shaft thrust plate 14 that slides on the thrust bearing 13 provided on the frame 23 and supports the thrust force acting on the crankshaft 32 is fixed to the end of the crankshaft 32. ..

This configuration will be explained concretely. At the end of the spindle portion 32a of the crankshaft 32, a shallow circular hole portion 32e for fitting the shaft thrust plate is formed on the swivel scroll 22 side of the eccentric hole 32b. On the other hand, the shaft thrust plate 14 is provided on the inner peripheral side of the disk portion 14a on which the thrust force acts by sliding on the thrust bearing 13, and projects in the axial direction of the hole portion 32e. A cylindrical convex portion 14b that fits with the inner peripheral surface is provided.

With this configuration, the shaft thrust plate 14 can be fixed to the top of the crankshaft 32 by fitting the convex portion 14b into the hole portion 32e by means such as press fitting. The lower surface of the disk portion 14a of the shaft thrust plate 14 slides on the thrust bearing 13 provided on the frame 23, whereby the thrust force acting on the crankshaft 32 is applied to the thrust bearing via the shaft thrust plate 14. Supported by 13.

Further, in this embodiment, the position of the convex portion 14b (the position of the fitting portion) and the position of the main bearing 27 (and the swivel bearing 28) do not overlap with each other in the axial direction (extension direction) of the crankshaft. That is, the convex portion 14b is configured to be positioned so as to be displaced in the axial direction with respect to the main bearing 27.

In the fitting portion between the convex portion 14b and the hole portion 32e, the crankshaft 32 may be pushed in the radial direction by the convex portion 14b of the inner shaft thrust plate 14 and expand and deform in the radial direction. However, as in this embodiment, the positions of the fitting portions of the crankshaft 32 and the shaft thrust plate 14 are shifted in the axial direction with respect to the main bearing 27 and the swivel bearing 28, and the positions of the convex portions 14b and the main bearing 27 are shifted. By setting the position of the above to a position that does not overlap in the axial direction of the crankshaft, it is possible to prevent the bearing gap from changing in the main bearing 27 and the swivel bearing 28. Therefore, the effect of appropriately maintaining the bearing gap in the main bearing or the like can be obtained.

That is, in this embodiment, the end of the crankshaft 32 is provided with a hole 32e for fitting the shaft thrust plate on the swivel scroll side of the eccentric hole 32b, and the inner diameter side of the shaft thrust plate 14 is provided. It has a convex portion 14b that fits with the inner peripheral surface of the hole portion 32e of the crankshaft 32, and the convex portion 14b is arranged at a position that does not overlap with the main bearing 27 in the axial direction. Therefore, even if the shaft thrust plate 14 is fitted to the end of the crankshaft 32 by press fitting or the like, it is possible to prevent the outer diameter of the crankshaft 32 facing the main bearing 27 from becoming large and the bearing gap from becoming small, which is appropriate. The effect of maintaining a large bearing gap can be obtained.

A refueling passage 32d is provided inside the crankshaft 32. During the operation of the scroll compressor 1, the pressure of the oil sump portion 12 is maintained at the approximate discharge pressure, and the lubricating oil is sucked up from the oil sump portion 12 through the oil supply passage 32d in the direction of the spindle portion 32a and reaches the eccentric hole 32b. .. The lubricating oil then passes through the gap of the swivel bearing 28, reaches the upper end side of the spindle 32a, and then passes through the oil groove 14c provided in the shaft thrust plate 14, and passes through the spindle 27 and the spindle. It passes through the gap of the portion 32a and finally flows out to the back pressure chamber 29 formed by the frame 23 and the swivel scroll 22 and the like.

A part of the back pressure chamber 29 communicates with the compression chamber 26, and the pressure of the back pressure chamber 29 is equal to or lower than the discharge pressure during the operation of the compressor. Therefore, the lubricating oil that has reached the eccentric hole 32b lubricates the sliding interface of the swivel bearing 28, the sliding interface between the thrust bearing 13 and the shaft thrust plate 14, and the sliding interface of the main bearing 27. It flows into the back pressure chamber 29 through the oil hole 27a formed in the lower part of the main bearing 27 and the oil hole 23a formed in the frame 23. The lubricating oil that has flowed into the back pressure chamber 29 lubricates the sliding portion of the old dam joint 24 and then flows to the compression chamber 26 side.
A seal 15 is provided to seal between the frame 23 and the swivel scroll 22, and restricts the lubricating oil from flowing out from the portion of the seal 15 to the back pressure chamber 29.

Next, the specific configuration of the shaft thrust plate 14 will be described with reference to FIG. FIG. 3 is a perspective view of the shaft thrust plate 14 shown in FIG. 2 as viewed from below. As shown in FIG. 3, the shaft thrust plate 14 has a cylindrical convex portion 14b that fits into a disk portion 14a having a sliding surface with the thrust bearing 13 and a hole portion 32e at the end of the crankshaft 32. It has. Further, on the sliding surface of the disk portion 14a, an oil groove 14c is provided in the radial direction so as to communicate the outer peripheral surface of the disk portion 14a and the space formed on the inner peripheral side of the thrust bearing 13. It is formed. That is, the oil groove 14c crosses the thrust sliding interface between the thrust bearing 13 and the shaft thrust plate 14, communicates with the outer peripheral side and the inner peripheral side of the sliding interface, and supplies lubricating oil to the disk portion. It is configured to flow from the outer peripheral side of 14a toward the main bearing 27.

The preferable position of the oil groove 14c will be described with reference to FIG. FIG. 4 is a perspective view of the upper part of the crankshaft shown in FIG. 1 as viewed from below, and is a view of a portion of the crankshaft 32 fixing the shaft thrust plate 14. In FIG. 4, 32f is a flat cut portion provided in the axial direction on the outer peripheral surface of the main shaft portion 32a of the

crankshaft

32, and 18 is a balance weight attached to the upper side of the rotor 31b in the crankshaft 32.

The gas compression load in the compression chamber 26 and the centrifugal force of the swivel scroll 22 and the balance weight 18 act on the crankshaft 32. Therefore, when the direction of the eccentric hole 32b is 0 °, the crankshaft 32 is located at any position from this 0 ° position to the rear side (reverse rotation direction) of 90 ° with respect to the rotation direction. Take a sloping posture.

In the example shown in FIG. 4, the flat surface cut portion 32f is provided in the eccentric direction on the outer peripheral surface of the spindle portion 32a (the direction in which the eccentric hole 32b is provided from the center of the crankshaft 32). The oil groove 14c is also provided in the eccentric direction, and is arranged at the same position in the circumferential direction as the flat surface cut portion 32f provided on the crankshaft 32.

The oil groove 14c and the flat surface cut portion 32f are not limited to those provided in the eccentric direction shown in FIG. 4, and are determined with reference to the inclination direction of the crankshaft 32 when the scroll compressor 1 is rotating at high speed and a high load is applied. Is good. That is, since one-sided contact is likely to occur at the sliding interface of the thrust bearing 13 in the inclined direction of the crankshaft 32, the formation of an oil film at the one-sided contact portion is promoted to maintain the oil film pressure in the inclined direction. Therefore, it is preferable not to provide the oil groove 14c in the inclination direction of the crankshaft 32, but to provide the oil groove 14c on the upstream side of the shear oil flow from the inclination direction.

The position where the oil groove 14c is provided will be described in detail. When the eccentric direction of the eccentric hole 32b is 0 ° in the main shaft portion of the crankshaft 32, from this 0 ° position to 90 ° (-90 °) on the rear side (the direction in which the rotation angle is negative) with respect to the rotation direction. The position of is in the direction in which the crankshaft 32 is inclined. That is, the inclination direction of the crankshaft 32 changes in the range from the above-mentioned 0 ° position to the −90 ° position according to the rotation speed.

Specifically, at low speed rotation, the tilting direction of the crankshaft 32 is greatly affected by the gas load of the compression chamber 26, and the crankshaft 32 is tilted in the direction of −90 °. As the rotation speed increases, the influence of the centrifugal force of the swivel scroll 22 and the balance weight 18 increases, and the inclination direction of the crankshaft 32 approaches the direction of the above-mentioned 0 ° position as the rotation speed increases.
The shaft thrust plate 14 also slides on the thrust bearing 13 provided on the frame 23 in a posture of being inclined in the same direction as the crankshaft 32 is inclined.

By providing one or more oil grooves 14c on the upstream side (front side in the rotation direction) with respect to the inclination direction of the crankshaft 32, the oil film pressure holding surface (the portion where the oil film pressure is generated) in the inclination direction of the crankshaft 32. ) Can be secured, and the lubricating oil can be easily flowed into the hydraulic pressure holding surface.

That is, since the oil groove 14c is provided on the sliding surface of the disk portion 14a of the shaft thrust plate 14, the lubricating oil flowing through the shaft thrust plate 14 preferentially flows through the oil groove 14c portion. Lubricating oil passing through the thrust bearing 13 easily flows into the one-sided contact portion of the thrust bearing 13 in the inclined direction of the crankshaft 32 due to the shear oil flow at the sliding interface of the thrust bearing 13, and the oil film formation of the one-sided contact portion is formed. Be promoted. As a result, the solid contact that tends to occur in the one-sided contact portion can be reduced, and the temperature rise due to frictional heat generation can also be reduced, so that friction loss and wear on the sliding surface of the thrust bearing 13 can be reduced.

Further, by fixing the shaft thrust plate 14 to the upper end portion of the crankshaft 32 and arranging the oil groove 14c on the sliding surface of the disk portion 14a of the shaft thrust plate 14, as the crankshaft 32 tilts, Although the gap between the shaft thrust plate 14 and the thrust bearing 13 fluctuates, by ensuring a sufficiently large cross-sectional area of the oil groove 14c, even if the crankshaft 32 is tilted, the sliding surface of the shaft thrust plate 14 Since the fluctuation of the amount of lubricating oil flowing on the main bearing 27 side can be suppressed to a small value, stable lubrication can be achieved.

The preferable position of the oil groove 14c will be specifically described. When the direction of the eccentric hole 32b is 0 °, if the oil groove 14c is provided at a position of 0 ° to 270 ° on the front side in the rotation direction, an oil film is provided in the inclination direction of the crankshaft 32 during operation of the scroll compressor 1. A pressure holding surface can be formed. Here, the farther the tilt direction of the crankshaft 32 is toward the rear in the rotational direction with respect to the position of the oil groove 14c, the more the lubricating oil supplied to the oil groove 14c is the portion of the crankshaft in the tilt direction (one-sided contact). The effect of flowing into the part) becomes smaller. Therefore, when the oil groove 14c is provided at a position of 0 ° to 180 ° (more preferably 0 ° to 90 °) forward in the rotation direction when the direction of the eccentric hole 32b is 0 °, the crank during operation is provided. The oil film pressure holding effect at the one-sided contact portion in the inclined direction of the shaft 32 can be further improved.

Further, if the range of the oil film pressure holding surface is secured within a range of ± 90 ° from the inclination direction of the crankshaft 32, a range in which the oil film pressure is generated can be sufficiently secured. It is preferable that 32f does not exist. Therefore, it is preferable that the oil groove 14c is provided in a range of 90 ° to 135 ° forward in the rotation direction from the inclination direction of the crankshaft 32 during operation. In particular, in the case of the variable rotation speed type scroll compressor 1, the oil groove is provided in the range of 90 ° to 135 ° forward in the rotation direction from the inclination direction of the crankshaft 32 at the time of high speed rotation, which is the highest load. Is good.

As described above, according to the present embodiment, the oil groove 14c is provided on the surface of the shaft thrust plate 14 that slides on the thrust bearing 13, and the oil groove 14c directs the direction of the eccentric hole 32b in the crankshaft 32. When it is set to 0 °, the crankshaft 32 is formed in the radial direction within 180 ° forward of the rotation direction of the crankshaft 32 from the 0 ° position, so that the crankshaft 32 is moved in the vertical direction due to deformation or inclination of the crankshaft 32. Even if the sliding interface of the thrust bearing 13 supported by the above is in a one-sided contact state, a scroll compressor capable of reducing wear can be obtained.

The material used for the shaft thrust plate 14 may be made of the same material as the crankshaft 32, but by making the shaft thrust plate 14 a material having a younger ratio than that of the crankshaft 32, the crankshaft 32 When the shaft is tilted, the shaft thrust plate 14 is easily deformed, and the one-sided contact of the shaft thrust plate 14 with the thrust bearing 13 can be reduced.

Further, in the present embodiment, the shaft thrust plate 14 is configured as a separate body from the crankshaft 32, and is fixed to the end of the crankshaft 32 when the scroll compressor 1 is assembled. As a result, when assembling the scroll compressor 1, it is possible to adjust and assemble the oil groove 14c so that the position of the oil groove 14c becomes an appropriate position according to the model. That is, depending on the model such as a high-speed scroll compressor or a constant-speed scroll compressor, or in the case of a variable-speed scroll compressor, the operating range is taken into consideration, and the position is suitable for each. It can be assembled so that the oil groove 14c is arranged. Therefore, since the same shaft thrust plate 14 can be used for a plurality of models of scroll compressors, it is possible to realize a highly efficient and highly reliable scroll compressor while reducing the manufacturing cost.

As described above, according to the present embodiment, since the same shaft thrust plate 14 can be adopted in the scroll compressor 1 of a plurality of models, the number of parts is reduced and the manufacturing cost is reduced, and the oil groove is reduced. The position of 14c can also be adjusted to an appropriate position. Further, since the position of the convex portion 14b of the shaft thrust plate 14 and the position of the main bearing 27 do not overlap in the axial direction, the bearing gap in the main bearing 27 can be appropriately maintained. Therefore, a scroll compressor with good performance can be realized.

Further, by assembling the shaft thrust plate 14 separately from the crankshaft 32, the crankshaft 32 can be inserted into the frame 23 from below at the time of assembly. Therefore, when assembling the scroll compressor 1, it is possible to assemble the closed container 4 without inverting it, and the man-hours for assembling the compressor can be reduced. Therefore, the manufacturing cost can be reduced from this aspect as well.
(Modification example 1)
Next, the modified example 1 in the above-described first embodiment will be described with reference to FIG. FIG. 5 is a diagram showing a modification 1 of the shaft thrust plate 14 shown in FIG. 2, which corresponds to FIG.
In this modification 1, the shaft thrust plate 14 is the same as the shaft thrust plate shown in FIG. 3 in that it has a disk portion 14a, a convex portion 14b, and an oil groove 14c.

The difference between the shaft thrust plate 14 in this modification 1 and that shown in FIG. 3 is that the shaft thrust plate 14 is provided with a through hole 14d penetrating in the axial direction. In the example shown in FIG. 3, a plurality of through holes 14d are provided at substantially constant intervals in the circumferential direction of the disk portion 14a. By providing the plurality of the through holes 14d in the disk portion 14a, the oil that lubricates the swivel bearing 28 shown in FIG. 2 is mainly passed through not only the oil groove 14c but also the through holes 14d from the swivel bearing 28 side. It can flow to the bearing 27 side. In this way, since it is possible to additionally secure a passage for the lubricating oil, it is possible to obtain an effect that the amount of oil supplied to the main bearing 27 side can be sufficiently secured and stabilized.

Further, according to the present modification 1, since a plurality of through holes 14d are provided in the disk portion 14a of the shaft thrust plate 14, it is possible to reduce the rigidity of the shaft thrust plate 14 and tilt the crankshaft 32. Occasionally, the shaft thrust plate 14 is deformed and comes into contact with the thrust bearing 13, so that the effect of reducing the one-sided contact of the shaft thrust plate 14 with the thrust bearing 13 can be obtained.
Other configurations are the same as those of the first embodiment, and the same effects as those of the first embodiment can be obtained.
(Modification 2)
The second modification of the first embodiment described above will be described with reference to FIG. FIG. 6 is a diagram showing a modification 2 of the shaft thrust plate shown in FIG. 2, which corresponds to FIG.
Also in this modification 2, the shaft thrust plate 14 is the same as the shaft thrust plate shown in FIG. 3 in that it has a disk portion 14a, a convex portion 14b, and an oil groove 14c.

The shaft thrust plate 14 in the second modification is different from the one shown in FIG. 3 in that the rigidity reducing groove 14e is provided in the circumferential direction of the sliding surface side (lower surface) of the disk portion 14a of the shaft thrust plate 14. Is. In the example shown in FIG. 6, the rigidity reducing groove 14e is composed of one circumferential groove, but a plurality of the rigidity reducing grooves 14e are provided in the circumferential direction on the sliding surface side of the disk portion 14a. It may be composed of a bottomed hole provided.

In the second modification, the rigidity of the shaft thrust plate 14 can be reduced by providing one of the rigidity reducing grooves 14e, and the shaft thrust plate 14 is deformed into the thrust bearing 13 when the crankshaft 32 is tilted. By contacting the shaft, the effect of reducing the one-sided contact of the shaft thrust plate 14 with the thrust bearing 13 can be obtained.

Further, according to the present modification 2, unlike the modification 1 shown in FIG. 5, the lubricating oil from the swivel bearing 28 side tends to concentrate in the oil groove 14c and flow easily, so that the lubricating oil easily flows to the sliding interface of the thrust bearing 13. It also has the effect of promoting refueling.
Other configurations are the same as those of the first embodiment, and the same effects as those of the first embodiment can be obtained.
(Modification example 3)
The modified example 3 in the above-described first embodiment will be described with reference to FIGS. 7 and 8. FIG. 7 is a diagram showing a modification 3 of the shaft thrust plate shown in FIG. 2, a perspective view of the shaft thrust plate 14 as viewed from above, and FIG. 8 is a diagram showing a scroll compressor using the shaft thrust plate shown in FIG. It is a figure corresponding to FIG.
Also in this modification 3, the shaft thrust plate 14 is the same as the shaft thrust plate shown in FIG. 3 in that it has a disk portion 14a, a convex portion 14b, and an oil groove 14c.

The difference between the shaft thrust plate 14 in this modification 3 and that shown in FIG. 3 will be described. The shaft thrust plate 14 in the third modification is provided with a mounting plate portion 14f integrally on the inner peripheral surface of the end portion (lower end portion) of the convex portion 14b. Further, the mounting plate portion 14f has a shape whose inner circumference is matched to the diameter of the eccentric hole 32b formed in the spindle portion 32a, and the mounting plate portion 14f has a crescent shape as a whole.

As shown in FIG. 7, the mounting plate portion 14f is provided with a plurality of mounting holes 14g. As shown in FIG. 8, the shaft thrust plate 14 has the mounting plate portion 14f attached to the end portion of the crankshaft 32 using a fixing screw 14h. Therefore, a screw hole for screwing the fixing screw 14h is also provided at the end of the spindle portion 32a.
Further, in the present modification 3, similarly to the modification 1 shown in FIG. 5, a plurality of through holes 14d are also provided at substantially constant intervals in the circumferential direction of the disk portion 14a.

According to the third modification, the shaft thrust plate 14 can be firmly fixed to the end of the crankshaft 32 by the fixing screw 14h, so that the reliability of the scroll compressor 1 can be improved and the scroll compressor 1 can be used for a long period of time. You can get a scroll compressor that can withstand. Further, according to the present modification 3, since the plurality of through holes 14d are provided in the circumferential direction of the disk portion 14a, the same effect as that of the modification 1 shown in FIG. 5 can be obtained.
Other configurations are the same as those of Example 1 described above, and the same effects as those of Example 1 can be obtained.

Example 2 of the scroll compressor of the present invention will be described with reference to FIGS. 9 and 10. FIG. 9 is a vertical cross-sectional view showing the scroll compressor of the second embodiment, and FIG. 10 is an enlarged cross-sectional view of a main part near the top of the crankshaft shown in FIG. In the description of the second embodiment, the parts having the same reference numerals as those of the first embodiment are the same or corresponding parts, and the same parts will be omitted and the parts different from the first embodiment will be mainly described.

In the scroll compressor 1 of the first embodiment shown in FIG. 1, the lubricating oil of the oil sump portion 12 is swirled by the swivel bearing 28 by using the pressure difference between the high pressure of the oil sump portion 12 and the back pressure chamber 29 which becomes a lower pressure. The differential pressure lubrication method for supplying to each sliding portion of the main bearing 27 and the like has been described. On the other hand, the scroll compressor 1 of the second embodiment is different from the first embodiment in that a positive displacement pump 16 is provided at the lower end of the crankshaft 32 to adopt a forced refueling system.

Further, in the second embodiment, instead of providing the oil hole 23a shown in FIG. 2, the frame 23 is provided with an oil drainage passage 23b having one end communicating with the lower part of the main bearing 27, in addition to the oil drainage passage 23b. As shown in FIG. 9, an oil drain pipe 17 is connected to the end side so that most of the oil supplied to the main bearing 27 is returned to the oil reservoir 12 at the bottom of the closed container 4. In this embodiment, the positive displacement pump 16 is composed of a trochoidal pump, but the present invention is not limited to this.
In this embodiment, the other configurations are the same as those in the first embodiment, and the configuration of the shaft thrust plate 14 is also the same as that shown in FIG.

With this configuration, when the scroll compressor 1 is driven and the crankshaft 32 rotates, the positive displacement pump 16 operates with the rotation of the crankshaft 32, and the lubricating oil of the oil sump portion 12 is the positive displacement type. It is supplied by the pump 16 to the oil supply passage 32d provided at the center of the crankshaft 32. From here, the lubricating oil flows into the eccentric hole 32b formed on the upper end side of the crankshaft 32.

The lubricating oil that has flowed into the eccentric hole 32b lubricates the sliding interface of the swivel bearing 28 that is inserted and fixed in the swivel shaft 22c, and then most of the lubricating oil is the disk portion of the shaft thrust plate 14 shown in FIG. After lubricating the sliding interface between the shaft thrust plate 14 and the thrust bearing 13, it flows to the sliding interface of the main bearing 27 through an oil groove 14c or the like formed on the lower surface of 14a. After lubricating the main bearing 27, the lubricating oil passes through the oil holes 27a formed in the lower part of the main bearing 27 and the oil drainage passage 23b formed in the frame 23, and the oil drainage pipe shown in FIG. It flows into 17, passes through the oil drain pipe 17, and is discharged to the oil sump portion 12.

Further, a part of the oil after lubricating the swivel bearing passes through the seal 15 provided between the frame 23 and the swivel scroll 22, flows out to the back pressure chamber 29, and slides the old dam joint 24 and the like. After lubricating the portion, it flows to the compression chamber 26 side.

According to the second embodiment, since the positive displacement pump 16 driven by the crankshaft 32 is configured to refuel each sliding portion, the amount of refueling increases as the rotation speed of the crankshaft 32 increases. In particular, a sufficient amount of oil is supplied to the thrust sliding interface during high-speed rotation. Therefore, bearing wear can be reduced by reducing the temperature rise due to frictional heat generation, and thus the reliability of the scroll compressor 1 can be further improved.

In each of the above-described embodiments of the present invention, the shaft thrust plate 14 and the thrust bearing 13 may be made of the same material, but at least the sliding surfaces of the shaft thrust plate 14 and the thrust bearing 13 may be formed. For either one, a material having excellent slidability, for example, a resin material such as tetrafluoroethylene resin (PTFE) or polyetheretherketone (PEEK), or a composite material containing them can be used, or a sintered material, brass, etc. Bronze, carbon material, etc. may be used. With this configuration, it is possible to reduce wear when solid contact occurs at the sliding interface of the thrust bearing 13.

Further, the thrust bearing 13 is attached to the frame 23 as a separate body from the frame 23, or when the frame 23 is made of cast iron such as FC250 (flake graphite cast iron), a part of the thrust bearing 13 is a bearing. It may be processed as a bearing sliding surface. As the cast iron material constituting the frame 23, FCD (spheroidal graphite cast iron), CV graphite cast iron, or the like can also be used. When the component itself of the frame 23 is used as a bearing, the sliding surface on the shaft thrust plate 14 side shall be made of a material having excellent slidability (resin, sintered material, brass, bronze, carbon material, etc.). As a result, wear can be reduced when solid contact occurs at the thrust sliding interface.

The present invention is not limited to the above-described examples, and includes various modifications. Further, it is possible to replace a part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment.
Furthermore, the above-described examples have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the described configurations.

1 ... scroll compressor, 2 ... compression mechanism, 3 ... drive, 4 ... closed container, 5 ... suction port, 6 ... discharge space, 7 ... space, 8 ... discharge pipe, 9 ... auxiliary bearing, 10 ... auxiliary bearing Housing, 11 ... Sub-frame, 12 ... Oil reservoir, 13 ... Thrust bearing, 14 ... Shaft thrust plate, 14a ... Disc, 14b ... Convex, 14c ... Oil groove, 14d ... Through hole, 14e ... Rigidity reduction groove , 14f ... Mounting plate, 14g ... Mounting hole, 15 ... Seal, 16 ... Positive displacement pump, 17 ... Oil drain pipe, 18 ... Balance weight, 21 ... Fixed scroll, 21a ... End plate, 21b ... Wrap, 21c ... Discharge Outlet, 22 ... swivel scroll, 21a ... end plate, 22b ... lap, 22c ... swivel shaft, 23 ... frame, 23a ... oil hole, 23b ... oil drainage passage, 24 ... old dam joint, 25 ... bolt, 26 ... compression chamber, 27 ... Main bearing, 27a ... Oil hole, 28 ... Swivel bearing, 29 ... Back pressure chamber, 31 ... Electric motor, 31a ... Stator, 31b ... Rotor, 32 ... Crank shaft, 32a ... Main shaft, 32b ... Eccentric hole, 32c ... Refueling pipe, 32d ... Refueling passage, 32e ... Hole, 32f ... Flat cut.

Claims

A closed container, a frame fixed to the closed container, a fixed scroll provided in the closed container and having an end plate and a spiral wrap standing on the end plate, and standing on the end plate and the end plate. A scroll compressor having a spiral wrap to be provided, a swivel scroll that meshes with the fixed scroll to form a compression chamber, and a crankshaft that swivels the swivel scroll.
A swivel shaft provided so as to project on the opposite side of the swivel scroll, an eccentric hole provided at the end of the crankshaft into which the swivel shaft is inserted, and an eccentric hole provided between the swivel shaft and the eccentric hole. The swivel bearing and the main bearing provided between the crankshaft and the frame and at substantially the same position in the axial direction as the swivel bearing.
A shaft thrust plate provided at the end of the crankshaft, a thrust bearing provided on the frame and sliding with the shaft thrust plate to support a thrust force acting on the crankshaft, and a thrust bearing.
The shaft thrust plate is provided with an oil groove provided on a surface sliding with the thrust bearing.
The oil groove is characterized in that it is formed in the radial direction at a position within 180 ° forward of the rotation direction of the crankshaft from the 0 ° position when the direction of the eccentric hole on the crankshaft is 0 °. Scroll compressor.
In the scroll compressor according to claim 1,
The scroll compressor, characterized in that the oil groove is formed at a position within 90 ° forward in the rotational direction of the crankshaft from the 0 ° position.
In the scroll compressor according to claim 1,
The scroll compressor is characterized in that the oil groove is provided in a range of 90 ° to 135 ° forward in the rotation direction from the inclination direction of the crankshaft during operation of the scroll compressor.
In the scroll compressor according to claim 3,
The scroll compressor is of a variable rotation speed type, and the oil groove is provided in a range of 90 ° to 135 ° forward in the rotation direction from the inclination direction of the crankshaft at the time of high-speed rotation, which is the highest load. A scroll compressor characterized by being present.
In the scroll compressor according to claim 1,
The shaft thrust plate is formed separately from the crankshaft and is fixed to the end of the crankshaft, and the shaft thrust plate is located at the end of the crankshaft on the swivel scroll side of the eccentric hole. A hole for fitting the crankshaft is provided, and a convex portion for fitting with the inner peripheral surface of the hole of the crankshaft is provided on the inner diameter side of the shaft thrust plate. , A scroll compressor characterized in that it is configured so that it does not overlap in the axial direction of the crankshaft.
A closed container, a frame fixed to the closed container, a fixed scroll provided in the closed container and having an end plate and a spiral wrap standing on the end plate, and standing on the end plate and the end plate. A scroll compressor having a spiral wrap to be provided, a swivel scroll that meshes with the fixed scroll to form a compression chamber, and a crankshaft that swivels the swivel scroll.
A swivel shaft provided so as to project on the opposite side of the swivel scroll, an eccentric hole provided at the end of the crankshaft into which the swivel shaft is fitted, and a swivel shaft and the eccentric hole provided. The swivel bearing and the main bearing provided between the crankshaft and the frame and at substantially the same position in the axial direction as the swivel bearing.
A shaft thrust plate provided at the end of the crankshaft, a thrust bearing provided on the frame and sliding with the shaft thrust plate to support a thrust force acting on the crankshaft, and a thrust bearing.
The shaft thrust plate is provided with an oil groove provided on a surface sliding with the thrust bearing.
The shaft thrust plate is formed separately from the crankshaft and is fixed to the end of the crankshaft, and the shaft thrust plate is located at the end of the crankshaft on the swivel scroll side of the eccentric hole. A hole for fitting the crankshaft is provided, and a convex portion for fitting with the inner peripheral surface of the hole of the crankshaft is provided on the inner diameter side of the shaft thrust plate. , A scroll compressor characterized in that it is configured so that it does not overlap in the axial direction of the crankshaft.
In the scroll compressor according to claim 5 or 6.
The shaft thrust plate includes a disk portion having a sliding surface with the thrust bearing and a cylindrical convex portion that fits with a hole portion at an end portion of the crankshaft, and the sliding surface of the disk portion. The scroll compressor is characterized in that the oil groove is formed in the radial direction so as to communicate the outer peripheral surface of the disk portion and the space formed on the inner peripheral side of the thrust bearing. ..
In the scroll compressor according to claim 1 or 6.
A scroll compressor characterized in that the shaft thrust plate is provided with a through hole penetrating in the axial direction.
In the scroll compressor according to claim 8,
A scroll compressor characterized in that a plurality of through holes provided in the shaft thrust plate are provided in the circumferential direction.
In the scroll compressor according to claim 1 or 6.
A circumferential rigidity reducing groove is provided on the sliding surface of the shaft thrust plate on the thrust bearing side, and the rigidity reducing groove is composed of one circumferential groove or a plurality of bottomed holes provided in the circumferential direction. A scroll compressor characterized by being present.
In the scroll compressor according to claim 7,
The shaft thrust plate is provided with a mounting plate portion integrally on the inner peripheral surface of the end portion of the convex portion, and the mounting plate portion has an inner circumference that matches the diameter of the eccentric hole, and the mounting plate portion is formed. , A scroll compressor characterized in that it is attached to the end of the crankshaft using a fixing screw.
In the scroll compressor according to claim 5 or 6.
A scroll compressor characterized in that the shaft thrust plate is made of a material having a Young's modulus smaller than that of the crankshaft.
In the scroll compressor according to claim 1 or 6.
A scroll compressor characterized in that at least a sliding surface of the shaft thrust plate is made of any one of a resin material, a sintered material, brass, bronze, and a carbon material.
In the scroll compressor according to claim 1 or 6.
An oil reservoir is formed at the bottom of the closed container, and the lubricating oil in the oil reservoir is supplied to the eccentric hole by a differential pressure lubrication method utilizing the pressure difference in the closed container. Compressor.
In the scroll compressor according to claim 1 or 6.
An oil sump is formed at the bottom of the closed container, a positive displacement pump is provided at the lower end of the crankshaft, and the lubricating oil of the oil sump is eccentric by a forced lubrication method by the positive displacement pump. A scroll compressor characterized by supplying to holes.