JPH11159484A - Scroll type fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reliably feed oil to an oil film pressure generating area by arranging an oil feeding cutout on an outer peripheral surface of an eccentric shaft part in a range of a specifc angle in the anti-rotational direction of a driving shaft from the eccentric direction of the eccentric shaft part to the driving shaft so as to reach an end surface. SOLUTION: A D-cut 1a being an oil feeding cutout arranged on an outer peripheral surface of an eccentric pin 1b, is arranged in an angle range θ of 30 deg. to 120 deg. in the anti-rotational direction of a crankshaft from the eccentric direction of the axis O2 of the eccentri pin 1b to the axis O1 of the crankshaft. This D-cut 1a is arranged so as to reach an upper end surface of the eccenetric pin 1b. Oil reaching the upper end of the eccentric pin part 1b mainly enters a slidingly movable part of the eccentric pin part 1b and a sliding bearing 5 from the D-cut 1a by passing through the upper end, and returns to an oil reservoir after lubrication. Therefore, the oil can be reliably fed to an oil film pressure generating area, and an increase in work manhours can be prevented since a required process is only to change an arranging position of an oil feeding cutout.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll type fluid machine, and more particularly to a scroll type fluid machine in which an outer peripheral surface of an eccentric shaft and a bearing portion of a movable scroll constitute a sliding portion. is there.

[0002]

2. Description of the Related Art Japanese Patent Application Laid-Open No. Hei 9-184 discloses a technique which focuses on a sliding portion between a bearing portion of a cylindrical boss portion connected to the back of a movable scroll and an eccentric pin portion at the upper end of a crankshaft.
492 and JP-A-8-200263. Hereinafter, the techniques described in JP-A-9-184492 and JP-A-8-200263 will be described as first and second conventional examples. Note that the names of the members disclosed in the above publication have been appropriately modified for convenience of explanation.

FIG. 17 is a schematic sectional view partially showing a first example of a conventional scroll type fluid machine. FIG.
FIG. 5 is an enlarged schematic view showing a configuration of an upper end surface of an eccentric pin portion at an upper end of a crankshaft.

Referring to FIG. 17 and FIG.
2, a motor M and a compression element CF are mainly disposed.

[0005] The motor M has a stator 8 fixed to the inner wall of the closed casing 12 and a rotor 9 facing the stator 8 at a predetermined interval. A crankshaft 101 is connected to the rotor 9. An eccentric portion 101b is provided at the upper end of the crankshaft 101. The eccentric pin portion 101b has a slide bush 10b.
2 is loosely fitted. The crankshaft 101 is provided with an oil supply passage 101d for guiding oil from an oil reservoir at the bottom of the sealed container 12 to the upper end of the eccentric pin portion 101b.

[0006] A compression element CF is provided so as to apply the rotational force of the crankshaft 101 via the slide bush 102.

[0007] The compression element CF has a movable scroll 3 and a fixed scroll 4. The movable scroll 3
End plate 3a, spiral tooth portion 3b projecting from the front surface of end plate 3a
And a boss 3c protruding from the back surface of the end plate 3a. The eccentric part 101b and the slide bush 102 are received in the boss part 3c,
The outer peripheral surface 2 and the inner peripheral surface of the boss 3c constitute a sliding portion. The fixed scroll 4 includes a head plate 4a and the head plate 4a.
And a spiral-shaped tooth portion 4b protruding therefrom. The spiral teeth 4b mesh with the spiral teeth 3b of the orbiting scroll 3 to form a compression chamber.

In such a scroll type fluid machine, oil is supplied from an oil reservoir at the bottom of the closed vessel 12 to an oil supply passage 101.
It is supplied to the sliding portion between the slide bush 102 and the boss portion 3c via d, but there is a possibility that the following lubrication problem may occur in this sliding portion. In other words, when lubrication is cut off transiently, when oil is extremely diluted with refrigerant, or until lubrication at start-up, when lubrication is reduced at low speed operation, fluid lubrication in the sliding bearing part occurs. Otherwise, wear and seizure may occur.

In the first conventional example, as shown in FIG. 18, a recess 102a for collecting and guiding the oil discharged from the oil supply passage 101d is provided on the upper end surface of the slide bush 102. The recesses 102a enable efficient lubrication of the lubricating portion, thereby preventing the above-described lubrication problems.

FIG. 19 is a schematic sectional view showing a second example of a conventional scroll type fluid machine. FIG. 20 corresponds to FIG.
9 is a schematic perspective view showing an enlarged configuration of an eccentric pin portion and a slide bearing in FIG.

Referring to FIGS. 19 and 20, in this scroll type fluid machine, a slide bush is not used, and eccentric pin portion 201b of crankshaft 201 is mounted on sliding bearing 5 on the inner peripheral surface of boss portion 3c. And directly constitute the sliding part. The crankshaft 201 is provided with an oil supply passage 201d for guiding oil from an oil reservoir at the bottom of the sealed container 12 to the upper end of the eccentric pin portion 201b. This eccentric pin portion 20
1b is provided with a notch 201a for refueling,
And a wedge-shaped groove 201e located on the circumferential side edge of the groove 1a.

The remaining structure is almost the same as that of the above-mentioned first conventional example. Therefore, the same members are denoted by the same reference numerals and description thereof will be omitted.

In the second conventional example, the oil flow in the circumferential direction of the outer periphery of the eccentric pin portion 201b can be made smooth by the wedge-shaped groove 201e, so that the above-mentioned lubrication problem can be prevented.

In addition to the first and second conventional examples, as a method of solving the above-described lubrication problem, a method of increasing the amount of oil supplied by an oil pump may be considered.

[0015]

However, each of the above-mentioned conventional examples has the following problems.

First, in the first conventional example, processing is required to provide a recess 102a on the upper end surface of the slide bush 102. For this reason, there is a problem that the number of processing steps is increased in manufacturing the scroll type fluid machine.

Also in the second conventional example, it is necessary to perform processing to provide a wedge-shaped groove 201e in addition to the oil supply notch 201a. Therefore, also in the second conventional example, there is a problem that the number of processing steps is increased in the manufacturing process of the scroll fluid machine.

Further, even if the method of increasing the amount of oil supplied by the oil pump is used, not only does the amount of oil rise during steady operation increase, but also there is a problem that there is no effect when the oil runs out.

An object of the present invention is to provide a scroll-type fluid machine that can effectively lubricate a lubricating section even in a poor lubricating environment without causing adverse effects such as an increase in the number of processing steps.

[0020]

According to a first aspect of the present invention, there is provided a scroll type fluid machine including a drive shaft and a movable scroll. The drive shaft has an eccentric shaft portion at an end and an oil supply opening on an end surface of the eccentric shaft portion. The orbiting scroll has a bearing part that forms a sliding part with the outer peripheral surface of the eccentric shaft part. An oil supply notch is provided on the outer peripheral surface of the eccentric shaft portion within a range of 30 ° or more and 120 ° or less in the counter-rotating direction of the drive shaft from the eccentric direction of the eccentric shaft portion with respect to the drive shaft so as to reach the end surface.

According to the scroll type fluid machine of the first aspect, the oil supply notch is provided within a range of 30 ° or more and 120 ° or less from the eccentric direction in the counter-rotating direction of the drive shaft.
This range is a region where no oil film pressure is generated in the sliding portion between the eccentric shaft portion and the bearing portion, and a region where the gap between the eccentric shaft portion and the bearing portion is relatively large, and This is a region where oil exists on the upper end surface.

Since the oil supply notch is provided in a region where the oil film pressure does not occur, the oil film pressure does not reduce the oil film pressure and does not lower the lubrication effect. Further, since the oil supply notch is provided in a region where the gap between the eccentric shaft portion and the bearing portion is relatively large, the passage resistance that oil receives from this gap is small. Therefore, the oil can be smoothly supplied to the oil film pressure generation region along the gap. Further, since an oil supply notch is provided in an area where oil exists on the upper end surface of the eccentric shaft portion, the oil that has come out of the oil supply opening is surely inserted into the gap between the eccentric shaft portion and the bearing portion through the oil supply notch. You can enter.

By providing the oil supply notch in the predetermined range as described above, the oil film pressure can be smoothly and reliably supplied to the oil film pressure generation region without reducing the lubrication effect due to the decrease in the oil film pressure. Therefore, it is possible to effectively supply oil to the lubrication unit even in a poor oil supply environment.

Further, since it is only necessary to change the arrangement position of the refueling notch to the above range, the number of processing steps does not increase.

The reason why the angle is set to 30 ° or more is that if the oil supply notch is provided in a range smaller than 30 °, the oil film pressure may be reduced and the lubricating effect may be reduced. In addition, the reason why the angle is set to 120 ° or less is that if the oil supply notch is provided in a range larger than 120 °, the gap between the eccentric shaft portion and the bearing portion becomes small, and the passage resistance received by the oil from this gap becomes large, so that it is smooth. This is because there is a possibility that the oil cannot be supplied to the oil film pressure generation region.

In the scroll type fluid machine according to the second aspect, the eccentric shaft portion has an eccentric pin portion integrally attached to an end of the drive shaft and a slide bush loosely fitted to the eccentric pin portion. doing. The refueling notch is provided on the outer peripheral surface of the slide bush.

According to the second aspect of the present invention, the present invention is applicable to a scroll type fluid machine having a slide bush.

In the scroll-type fluid machine according to the third aspect, a rounding or chamfering process is performed on a circumferential end of the oil supply notch.

According to the scroll type fluid machine according to the third aspect, it is possible to more smoothly supply oil from the oil supply notch in the circumferential direction by the R processing or the chamfering processing.

In the scroll-type fluid machine according to the fourth aspect, the peripheral portion where the end surface of the eccentric shaft portion and the outer peripheral surface intersect is chamfered.

According to the scroll-type fluid machine according to the fourth aspect, it is possible to smoothly supply the oil that has come out of the oil supply opening from the end face of the eccentric shaft portion to the outer peripheral face by chamfering.

In the scroll type fluid machine according to the fifth aspect, the upper end surface of the eccentric pin portion where the oil supply opening is provided is located higher than the upper end surface of the slide bush.

According to the scroll type fluid machine of the fifth aspect, since the upper end surface of the eccentric pin portion is located at a position higher than the upper end surface of the slide bush, it is not necessary for the oil to climb over the upper end surface of the slide bush, so that the oil can smoothly flow. Oil can be supplied to the outer peripheral side of the slide bush.

In the scroll type fluid machine according to the present invention, a groove is formed on the end face of the eccentric shaft portion from the oil supply opening to the oil supply notch direction.

According to the scroll-type fluid machine of the sixth aspect, since the oil can be guided in the direction of the oil supply notch by the groove, the oil can be efficiently guided to the oil supply notch.

[0036]

Embodiments of the present invention will be described below with reference to the drawings.

Embodiment 1 FIG. 1 is a sectional view schematically showing a configuration of a scroll compressor according to Embodiment 1 of the present invention. Referring to FIG.
In the sealed container 12, a motor M and a compression element CF are mainly disposed.

The motor M has a stator 8 fixed to the inner wall of the closed casing 12, and a rotor 9 facing the stator 8 at a predetermined interval. The crankshaft 1 is connected to the rotor 9. This crankshaft 1
An eccentric pin portion 1b eccentric with respect to the crankshaft 1 is provided at the upper end portion of the shaft. An oil supply passage (not shown) is provided in the crankshaft 1 to pass oil from the oil sump at the bottom of the scroll compressor to the upper end surface of the eccentric pin 1b. A D-cut 1a is provided on the outer peripheral surface of the eccentric pin 1b. A compression element CF is provided so that a rotational force can be applied from the eccentric pin portion 1b of the crankshaft 1.

The compression element CF has a movable scroll 3 and a fixed scroll 4. The movable scroll 3
End plate 3a, spiral tooth portion 3b projecting from the front surface of end plate 3a
And a boss 3c protruding from the back surface of the end plate 3a. An eccentric pin portion 1b is received in the boss portion 3c, and an outer peripheral surface of the eccentric pin portion 1b and a slide bearing 5 constituting a sliding portion are attached to the inner peripheral surface of the boss portion 3c. The orbiting scroll 3 is supported by, for example, an Oldham coupling so as to revolve while receiving its rotational force from the crankshaft 1 while keeping its attitude relatively. The fixed scroll 4 has a head plate 4a and a spiral tooth 4b protruding from the head plate 4a. The spiral teeth 4b mesh with the spiral teeth 3b of the orbiting scroll 3 to form a compression chamber. The fixed scroll 4 is fastened and fixed to the upper housing 6 by, for example, bolts.

The crankshaft 1 is connected to the upper housing 6
And a bearing (not shown) provided in a lower housing (not shown). The crankshaft 1 is provided with a balance weight 1c for balancing rotation. The upper housing 7 and the lower housing are mutually closed container 1
It is fixed to 2.

The closed vessel 12 is provided with a suction pipe 10 for sucking the refrigerant gas from the outside to the inside, and a discharge pipe 11 for discharging the refrigerant gas from the inside to the outside.

Of particular note in the configuration of this scroll compressor is the arrangement position of a so-called D-cut 1a provided on the outer peripheral surface of the eccentric pin portion 1b. This arrangement position will be described below with reference to FIG.

FIG. 2 is a schematic sectional view taken along line D ₁ -D _{1 of} FIG. 1 showing the configuration of the sliding portion between the eccentric pin portion and the slide bearing. Referring to FIG. 2, the D-cut 1 a extends from the eccentric direction of the center axis O ₂ of the eccentric pin portion _{1 a with} respect to the center axis O ₁ of the crank shaft 1 (rightward in the drawing along the line AA). 1 in an anti-rotational direction (clockwise in the figure) within an angle range θ of 30 ° or more and 120 ° or less. Also this D cut 1
a is provided so as to reach the upper end surface of the eccentric pin portion 1a.

Next, the operation of the scroll compressor shown in FIG. 1 will be described. Referring to FIG. 1, when the motor M is energized, the rotor 9 rotates, and this rotational force is applied to the movable scroll 3 via the eccentric pin portion 1 b of the crankshaft 1. The orbiting scroll 3 orbits while keeping its attitude relatively by, for example, an Oldham coupling.

The revolving of the movable scroll 3 causes the spiral teeth 3 of the movable scroll 3 and the fixed scroll 4 to rotate.
The compression chamber constituted by b and 4b moves from the outer peripheral side to the inner peripheral side while gradually reducing the volume. Thereby, the refrigerant gas introduced into the closed container 12 by the suction pipe 10 and reaching the outermost compression chamber is gradually compressed and reaches the innermost compression chamber, where it is discharged from the discharge port 4c. .
The refrigerant gas discharged from the compression element CF is discharged to the outside of the closed container 12 by the discharge pipe 11.

During this operation, the oil is pushed up in the oil supply passage (not shown) in the crankshaft 2 by centrifugal force or a pump from an oil reservoir at the bottom of the closed container 12. Eccentric pin part 1b
The oil that has reached the upper end surface passes through the upper end surface and mainly enters the sliding portion between the eccentric pin portion 1b and the sliding bearing 5 from the D cut 1a, and after lubricating the sliding portion, falls down. And return to the sump.

Next, the process in which the inventors of the present invention can derive the angle range θ in which the D cut 1a is arranged will be described in detail.

FIG. 3 is a view for explaining the bearing load, and is a sectional view corresponding to the section of FIG. Referring to FIG. 3, during operation of the scroll compressor according to the present embodiment, a radial gas load Fr, a tangential gas load Ft, and a centrifugal load Fi are mainly applied to the center O ₂ of the orbiting scroll 3. Works. The radial gas load Fr and the tangential gas load Ft are loads generated by the refrigerant gas in the compression chamber compressed by the compression element CF.

The radial gas load Fr is a load that tries to peel off the eccentric direction of the movable scroll 3 (that is, the center O ₂ of the movable scroll 3 is
₁ ), which is a load acting in the radial direction of the trajectory of the orbital motion of the orbiting scroll 3. The tangential gas load Ft is a load acting in the tangential direction of the orbit of the orbiting motion of the orbiting scroll 3.
This is a load that tries to hinder the rotation of. In addition, centrifugal load Fi
Works from the center O ₂ of the movable scroll 3 toward the outer periphery.

A load F, which is the resultant of the loads Ft, Fr and Fi, is applied to the center O ₂ of the orbiting scroll 3, and this load F is used as a bearing load as the sliding bearing 5 and the eccentric pin 1b.
Will act on the sliding part.

When the bearing load F is applied to the sliding portion of a normal journal bearing, as shown in FIG.
, The maximum and minimum gap positions are spatially determined on a straight line EE forming an angle φ in the rotation direction of the shaft 301. That is,
The center O _{2 of the} shaft 301 is eccentric along the straight line EE with respect to the center O _{3 of the} bearing 302. Then, the oil film pressure distribution exists in a range of 180 ° in the anti-rotation direction of the shaft 301 from the position of the minimum gap (that is, up to the position of the maximum gap).

In the above description, the angle φ is called an eccentric angle, and details thereof are described in, for example, “Mechanical Engineering Handbook”, written by the Japan Society of Mechanical Engineers.
Issue, pp. B1-35 to B1-37.

[0053] Thus, in FIG. 2, and the oil film thickness becomes minimum in a linear E-E point R ₁ on a line forming an angle φ in the rotational direction of the crank shaft 1 from the load line C-C, a gap at the point R ₂ maximum Become. Then, the position R of the minimum oil film thickness
So that the oil film pressure distribution is present in the range of 180 ° from _one to the anti-rotation direction of the crank shaft 1 (i.e. to the position R ₂ of the maximum gap). Note that, for convenience of description, the center point of the slide bearing 5 is omitted in FIG.

For example, if the oil supply opening 1d is provided at the position shown in FIG. 4, the oil discharged from the oil supply opening 1d is distributed in the hatched area on the upper end surface of the eccentric pin portion 1b. .

In the present embodiment, the following items (1) to (3) are taken into consideration in determining the formation position of the D cut 1a.

(1) The D cut 1a is an eccentric pin 1b
It should be arranged in a region between the (crankshaft 1) and the slide bearing 5 where no oil film pressure occurs. When the D cut 1a is provided in the oil film pressure generating region, the gap between the eccentric pin portion 1b and the slide bearing 5 (bearing gap) becomes large due to the formation of the D cut 1a, so that the oil film pressure is reduced and the lubrication effect is reduced. This is because that.

(2) The D cut 1a should be arranged in a wide area of the bearing gap. This is because, in a wide bearing gap, the passage resistance received by the oil is small, so that the oil can smoothly move in the circumferential direction and reach the oil film pressure generation region.

(3) The D cut 1a is an eccentric pin 1b
The top surface should be located in the area where the oil is present.
This is because even if the D cut 1a is provided in a region where the oil does not exist on the upper end surface of the eccentric pin portion 1b, oil cannot be supplied from the D cut 1a into the bearing gap, and there is no point in providing the D cut 1a. .

The inventors of the present application have made the following studies in order to check the optimal arrangement position of the D cut 1a.

The above examination was performed by obtaining the eccentric angle φ under each condition and deriving the minimum gap angle b and the maximum gap angle c shown in FIG. 2 from the eccentric angle φ. Here, the bearing load direction a is an angle between the normal line BB of the eccentric direction and the load line CC in FIG. Also a minimum clearance angle b is the angle from the normal B-B to the oil film thickness minimum position R _1, and the maximum clearance angle c is the angle from the eccentric direction A-A to a maximum gap position R _2. Each condition A to C in the above study
Is as follows.

A: The condition in which the bearing load direction a in FIG. 2 is the maximum B: The condition in which the bearing load direction a is the minimum C: The condition that frequently occurs in actual operation The eccentric angle φ obtained as a result of this study, Table 1 shows the minimum clearance angle b and the maximum clearance angle c.

[0062]

[Table 1]

By considering this result from the viewpoints of the above (1) to (3), the lower limit and the upper limit of the angle range θ are derived as shown in the following (i) and (ii).

(I) Regarding the lower limit value (30 °) of the angle range θ As described with reference to FIG. 2, the oil film pressure is the angle range of 180 ° from the minimum position R ₁ of the oil film thickness to the maximum gap position R _2. Occurs at 135 ° from the minimum position R ₁ of the oil film thickness.
It becomes extremely small in the angle range of up to 180 °. That is,
If the angle range is 135 ° or more from the minimum gap position, the oil film pressure is not impaired even if the D cut 1a is provided.
When this angle range is converted into an angle range from the eccentric direction (the right direction in the drawing of the line AA) under the condition B, 75 °-
(180 ° -135 °) = 30 °. That is, this means that the oil film pressure is not impaired if the D cut 1a is provided at a position of 30 ° or more from the eccentric direction in the anti-rotation direction of the crankshaft 1.

The reason why the condition B was used in deriving the above-mentioned angle range is that the condition B is a condition that maximizes the maximum gap angle c. That is, if the angle range (30 ° or more) is obtained under the condition B, the effective range of the oil film pressure does not fall within this angle range even under the other conditions A and C.

(Ii) Upper limit of angle range (120 °) On the other hand, as described above, the D cut 1a should be provided in a wide area of the bearing gap. The problem that the passage resistance does not occur even when the D cut 1a is provided is within an angle range of ± 90 ° from the maximum gap angle c. Therefore, the upper limit of the angle range for securing a sufficient bearing gap under condition A is 30 ° + 90 ° = 120 °.

The reason for using the condition A in deriving the above angle range is that the condition A is a condition that minimizes the maximum gap angle c. That is, if the angle range (120 ° or less) is obtained under this condition A, the problem of the passage resistance will not occur even in the other conditions B and C as long as it is within this angle range.

From the above, as the angle range in which the D cut 1a is provided, 30 ° or more and 120 ° or less in the counter-rotating direction of the crankshaft 1 from the eccentric pin direction are derived.

The angle range θ of 30 ° or more and 120 ° or less is located in the region where the oil exists on the upper end face of the eccentric pin portion 1b, as apparent from comparison with FIG. For this reason, if the oil supply opening 1d is provided at a position as shown in FIG. 4, for example, the oil discharged from the oil supply opening 1d can be reliably inserted into the D cut 1a.

In the scroll compressor according to the present embodiment, D
By setting the position of the cut 1a at 30 ° or more from the eccentric direction, the oil film pressure is not impaired, so that a reduction in the lubrication effect can be prevented. In addition, since the arrangement position of the D cut 1a is set to 120 ° or less from the eccentric direction, a bearing gap that does not cause a problem in passage resistance can be secured, and lubrication can be smoothly performed from the D cut 1a in the circumferential direction. . Therefore, the lubrication effect is not reduced due to the loss of the oil film pressure, and the oil can be smoothly and reliably supplied to the oil film pressure generation region, so that the oil can be effectively supplied to the lubrication section even in a poor oil supply environment. Become.

Further, since it is only necessary to change the arrangement position of the D cut 1a within the angle range θ, the number of processing steps does not increase.

In this embodiment, the case where the slide bush is not used has been described. However, the present structure can be similarly applied to the case where the slide bush is used.

FIG. 5 is a partial sectional view schematically showing the structure of a scroll compressor using a slide bush. FIG. 6 is a sectional view taken along line D ₂ -D ₂ in FIG.

Referring mainly to FIG. 5, in this structure, slide bush 2 is loosely fitted to eccentric pin portion 1b of crankshaft 1. The slide bush 2 has a cylindrical portion 2b that is loosely fitted to the eccentric pin portion 1b.
For example, a flange 2c and a balance weight 2
d is attached. Further, the crankshaft 1 has, for example, a flange 1e so as to support the flange 2c of the slide bush 2 from below. The torque of the crankshaft 1 is transmitted to the movable scroll 3 via the slide bush 2.
Therefore, the outer peripheral surface of the slide bush 2 and the slide bearing 5 constitute a sliding portion.

Referring mainly to FIG. 6, a D-cut 2a is arranged on the outer peripheral surface of the slide bush 2 within the same angular range θ as described above. That is, the D cut 2a is provided within an angle range θ of 30 ° or more and 120 ° or less in the counter-rotating direction of the crankshaft 1 from the eccentric direction of the eccentric pin portion 1b (the right direction in the drawing of the line AA).

The other structure is substantially the same as the structure shown in FIGS. 1 and 2 described above, and the same members are denoted by the same reference characters and description thereof will not be repeated.

Even when the slide bush 2 is used as described above, if the D cut 12a is provided within the above-mentioned angle range θ, the oil film pressure can be smoothly and reliably supplied to the oil film pressure generation region without damaging the oil film pressure. Therefore, it is possible to effectively lubricate the lubricating part even in a poor lubrication environment. Also, the number of processing steps does not increase.

Embodiment 2 FIG. 7 is a schematic sectional view showing a D-cut shape of a scroll compressor according to Embodiment 2 of the present invention.

[0079] With reference to FIG. 7, in this exemplary aspect, R processed into circumferential end portion S ₁ of the D-cut 1a provided on the outer peripheral surface of the eccentric pin portion 1b (or chamfering) is applied. Further, since such an R shape can be formed at the same time as the outer peripheral finishing (paper wrapping or the like) of the eccentric pin portion 1b, it does not lead to an increase in the number of processing steps.

Also in the conventional example shown in FIG. 8, since the above-described outer peripheral finishing is performed, it is conceivable that the peripheral ends S ₁ and S ₂ of the D-cut become R-shaped by this processing. However, when the above-mentioned processing is performed without intending to form the R shape, the circumferential ends S ₁ , S _{1
Even if 2} has an R shape, its R dimension is R0.1 or less.

On the other hand, in the present embodiment, an R-shape is positively formed during the above-mentioned finishing. Therefore, the R dimension is larger than R0.1, for example, R3 and R5. By thus a large dimension R and R3 above, the passage gap in the circumferential end portion S ₁ of the D-cut 1a as shown in Table 2 below is approximately 3 times more in the case of R0.1.

[0082]

[Table 2]

Thus, in the present embodiment, the oil that has exited from the oil supply opening 1d and has reached the oil supply notch 1a passes through a large passage gap, so that it can smoothly reach the oil film pressure generation region.

In this embodiment, the R processing or the surface
The chamfering is performed at the end S on the rotation direction side of the crankshaft 1.₁only
The end S_TwoOnly or end S₁And
And S _TwoMay be applied to both.

Since the ends S ₁ , S ₂ of the D-cut 1 a are rounded or chamfered, even if the ends S ₁ , S ₂ collide with the sliding bearing 5 at the time of starting, the sliding bearing 5 is not moved. Scratching can be prevented.

Also, as shown in FIG. 9, even when the slide bush 2 is loosely fitted to the eccentric pin portion 1b, the circumferential ends S ₁ , S _{1 of} the D cut 2a provided on the outer periphery of the slide bush 2 are also provided. _If R processing or chamfering is applied to 2, the same effect as above can be obtained. FIG. 9 shows the circumferential end S
₁ shows a configuration in which R processing is performed only.

Third Embodiment FIG. 10 is a partial sectional view showing the configuration of the upper end of an eccentric pin portion of a scroll compressor according to a third embodiment of the present invention. Referring to FIG. 10, in the present embodiment, a chamfering process is performed on a peripheral portion where an outer peripheral surface and an upper end surface of eccentric pin portion 1b intersect.

The remaining structure is almost the same as that of the first embodiment, so that the same members are denoted by the same reference numerals and description thereof will be omitted.

In this embodiment, since the peripheral edge of the eccentric pin portion 1b is chamfered, the lubrication opening 1d is compared with the configuration in which the chamfering is not performed (FIG. 11).
It is easy to supply the oil which has come out to the sliding portion between the eccentric pin portion 1b and the sliding bearing 5.

The configuration in which such chamfering is performed is an effective configuration for supplying oil to the sliding portion from the entire circumference of the upper end surface of the slide bush.

Also, as shown in FIG. 12, even when the slide bush 2 is loosely fitted to the eccentric pin portion 1b, by chamfering the periphery of the slide bush 2,
It becomes easy to supply oil to the sliding part.

Fourth Embodiment FIG. 13 is a schematic sectional view showing the configuration of the upper ends of an eccentric pin portion and a slide bush of a scroll compressor according to a fourth embodiment of the present invention. Referring to FIG. 13, in the present embodiment, the upper end surface of eccentric pin portion 1 b is located higher than the upper end surface of slide bush 2 in a state where slide bush 2 is loosely fitted to eccentric pin portion 1 b.

The remaining structure is almost the same as that of the first embodiment, so that the same members are denoted by the same reference numerals and description thereof will be omitted.

As shown in FIG. 14, when the upper end surface of the eccentric pin portion 1b is lower than the upper end surface of the slide bush 2, the oil coming out of the oil supply opening 1d reaches the sliding portion in order to reach the sliding portion. Have to get over. For this reason, in the configuration of FIG. 14, it is not possible to sufficiently supply oil to the sliding portion between the slide bush 2 and the slide bearing 5 in a poor oil supply environment.

On the other hand, in the present embodiment, the upper end surface of the eccentric pin portion 1b is located higher than the upper end surface of the slide bush 2 as shown in FIG. For this reason, it is not necessary for the oil discharged from the oil supply opening 1d to climb over the upper end surface of the slide bush 2. Therefore, it is possible to supply sufficient oil to the sliding portion between the slide bush 2 and the slide bearing 5 even in a poor oil supply environment.

Fifth Embodiment FIG. 15 is a diagram showing a configuration of an upper end surface of an eccentric pin portion of a scroll compressor according to a fifth embodiment of the present invention. FIG.
5, in the present embodiment, a groove 1f is provided on the upper end surface of the eccentric pin portion 1b. The groove 1f is formed so as to reach the D cut 1a from the oil supply opening 1d.

The remaining structure is almost the same as that of the first embodiment, and therefore the same members are denoted by the same reference characters and description thereof will not be repeated.

By providing such a groove 1f, the oil that has come out of the oil supply opening 1d can be guided to the D cut 1a, so that the oil can be efficiently guided to the D cut 1a.

Also, as shown in FIG. 16, when the slide bush 2 is loosely fitted to the eccentric pin 1b, the D cut 1
By providing the groove 1f toward a, the same effect as described above can be obtained.

In the first to fifth embodiments described above, the scroll compressor has been described. However, the present invention is not limited to the scroll compressor, but can be applied to a scroll expander.

The embodiments disclosed this time are to be considered in all respects as illustrative and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

[0102]

According to the first aspect of the present invention, the oil supply notch has an angle of 30 ° or more from the eccentric direction to the anti-rotation direction of the drive shaft.
It is provided within a range of 20 ° or less. For this reason, this oil supply notch does not reduce the oil film pressure and reduce the lubrication effect. Further, since the passage resistance of the oil received from the gap between the eccentric shaft portion and the bearing portion can be reduced, the oil can be smoothly supplied to the oil film pressure generating region along the gap.
Furthermore, since the oil supply notch is provided in the region where the oil exists on the upper end surface of the eccentric shaft portion, the oil that has come out of the oil supply opening is surely inserted into the gap between the eccentric shaft portion and the bearing portion through the oil supply notch. You can enter.

Further, since it is only necessary to change the arrangement position of the refueling notch to the above range, the number of processing steps does not increase.

The reason why the angle is set to 30 ° or more is that if an oil supply notch is provided in a range smaller than 30 °, the oil film pressure may be reduced and the lubricating effect may be reduced.
The reason why the angle is set to 120 ° or less is that if the oil supply notch is provided in a range larger than 120 °, the gap between the eccentric shaft portion and the bearing portion becomes small and the passage resistance received by the oil becomes large, so that the oil film pressure is smoothly increased. This is because there is a possibility that oil cannot be supplied to the generation area.

According to the second aspect of the present invention, the present invention is applicable to a scroll type fluid machine having a slide bush.

According to the third aspect of the present invention, since the round end or the chamfering process is performed on the circumferential end of the fuel supply notch, the lubrication can be smoothly performed in the circumferential direction from the fuel supply notch. It becomes possible.

According to the fourth aspect of the present invention, since the peripheral portion of the eccentric shaft portion is chamfered, the oil coming out of the oil supply opening by this chamfering process is removed from the end face of the eccentric shaft portion to the outer periphery. It is possible to lubricate the surface smoothly.

According to the fifth aspect of the present invention, since the upper end surface of the eccentric pin portion is located higher than the upper end surface of the slide bush, it is possible to smoothly supply oil to the outer periphery of the slide bush.

According to the sixth aspect of the present invention, since a groove is formed in the end face of the eccentric shaft portion from the oil supply opening in the oil supply notch direction, oil is guided to the oil supply notch by this groove. It is possible to efficiently guide the oil to the oil supply notch.

[Brief description of the drawings]

FIG. 1 is a partial cross-sectional view schematically showing a configuration of a scroll compressor according to an embodiment of the present invention.

FIG. 2 is a schematic sectional view taken along line D ₁ -D ₁ of FIG.

FIG. 3 is a diagram for explaining that a bearing load is applied to a sliding portion between an eccentric pin portion and a slide bearing.

FIG. 4 is a schematic cross-sectional view of the journal bearing for explaining the maximum and minimum oil film thickness positions in the journal bearing.

FIG. 5 is a partial cross-sectional view showing a case where the configuration of the first embodiment of the present invention is applied to a scroll compressor having a slide bush.

FIG. 6 is a schematic sectional view taken along line D ₂ -D ₂ of FIG. 5;

FIG. 7 is a schematic sectional view illustrating a configuration of an eccentric pin portion of a scroll compressor according to Embodiment 2 of the present invention.

FIG. 8 is a schematic sectional view showing a configuration in which a circumferential end of a D-cut is not subjected to chamfering.

FIG. 9 is a cross-sectional view illustrating a configuration when the configuration of the second embodiment is applied to a scroll compressor having a slide bush.

FIG. 10 is a partial cross-sectional view showing a configuration near an upper end portion of an eccentric pin portion of a scroll compressor according to Embodiment 3 of the present invention.

FIG. 11 is a schematic cross-sectional view showing a configuration in which a peripheral portion of an eccentric pin portion is not chamfered.

FIG. 12 is a schematic cross-sectional view showing a configuration when the configuration of the third embodiment is applied to a scroll compressor having a slide bush.

FIG. 13 is a schematic cross-sectional view showing a configuration near an upper end surface of an eccentric pin portion and a slide bush of a scroll compressor according to Embodiment 4 of the present invention.

FIG. 14 is a schematic cross-sectional view showing a configuration in which an upper end surface of an eccentric pin portion is at a position lower than an upper end surface of a slide bush.

FIG. 15 is a diagram showing a configuration of an upper end surface of an eccentric pin portion of a scroll compressor according to Embodiment 5 of the present invention.

FIG. 16 is a diagram showing a configuration when the configuration of the fifth embodiment is applied to a scroll compressor having a slide bush.

FIG. 17 is a partial sectional view showing a first example of a conventional scroll compressor.

18 is a view showing the upper end surfaces of the eccentric pin portion and the slide bush shown in FIG.

FIG. 19 is a schematic sectional view showing a second example of a conventional scroll compressor.

20 is a perspective view showing a configuration of a wedge-shaped groove formed in the eccentric pin portion shown in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Crankshaft 1a D cut 1b Eccentric pin part 2 Slide bush 2a D cut 2b cylinder part 3 Movable scroll 5 Slide bearing

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Toshiaki Yoshii 3-12 Chikushinmachi, Sakai-shi, Osaka Daikin Industries Co., Ltd. Inside the seaside factory (72) Inventor Keiji Yoshimura 3-12 Chikushinmachi, Sakai-shi, Osaka Daikin Industries, Ltd. Sakai Factory Rinkai Plant (72) Inventor Takashi Kamikawa 3-12 Chikushinmachi, Sakai City, Osaka Daikin Industries, Ltd. Sakai Factory Rinkai Factory

Claims (6)

[Claims] 1. A drive shaft (1) having an eccentric shaft (1b, 2) at an end and an oil supply opening (1d) at an end face of the eccentric shaft (1b, 2); A movable scroll (3) having a bearing part (5) that forms a sliding part with the outer peripheral surface of the part (1b, 2); and the eccentric shaft part (1b) with respect to the drive shaft (1). Notch (1a, 2a) in the outer peripheral surface of the eccentric shaft portion (1b, 2) within the range of 30 ° or more and 120 ° or less in the anti-rotation direction of the drive shaft (1) from the eccentric direction of 2). Is provided so as to reach the end face. 2. The eccentric shaft portion (1b, 2) has an eccentric pin portion (1) integrally attached to an end of the drive shaft (1).
b) and a slide bush (2) loosely fitted to the eccentric pin portion (1b), and the refueling notch (2a) is provided in the slide bush (2).
The scroll type fluid machine according to claim 1, wherein the scroll type fluid machine is provided on an outer peripheral surface of the scroll type fluid machine. 3. The scroll-type fluid machine according to claim 1, wherein a rounding or chamfering process is performed on a circumferential end of the oil supply notch (1a, 2a). 4. The scroll-type fluid machine according to claim 1, wherein a peripheral portion of the eccentric shaft portion (1b, 2) where the end surface and the outer peripheral surface intersect is chamfered. 5. The eccentric pin portion (1b) according to claim 2, wherein an upper end surface provided with the oil supply opening (1d) is located at a position higher than an upper end surface of the slide bush (2). Scroll type fluid machine. 6. The oil supply notch (1) is formed in the end face of the eccentric shaft portion (1b, 2) through the oil supply opening (1d).
a, a groove (1f) directed toward the 2a) direction is formed;
The scroll type fluid machine according to claim 1.