JP6598881B2 - Scroll compressor - Google Patents

Description

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

Conventionally, in air conditioners, refrigerators, and the like, for example, scroll compressors are used (see, for example, Patent Document 1).
In this scroll compressor, when the refrigerant gas is sucked into the sealed shell from the suction pipe, the refrigerant gas is sucked into a compression portion constituted by a fixed scroll, an orbiting scroll, and the like disposed at an upper portion in the shell. When the scroll compressor is energized, torque is generated in the rotor and the stator that constitute the electric mechanism disposed at the lower portion of the compressor, and the swing having a rotational center that is eccentric with respect to the center of the fixed scroll. The main shaft connected to the dynamic scroll rotates.
As a result, the orbiting scroll coupled to the main shaft performs an orbiting motion, and the refrigerant gas sucked into the compression mechanism portion is compressed in cooperation with the fixed scroll. The compressed refrigerant gas is discharged out of the shell through the discharge pipe.

In such a scroll compressor, an eccentric shaft portion is formed at the upper end of the main shaft. Further, a rocking bearing is formed on the lower surface side of the rocking scroll, and a slider provided with a slit is accommodated in the rocking bearing.
An eccentric shaft portion of the main shaft is inserted into the slit of the slider.

JP 2013-245 566 A

However, the conventional scroll compressor does not have a structure that restricts the slider from moving in the axial direction, so that the slider floats during operation of the scroll compressor.
When the slider is lifted in this way, the upper end of the slider slides in contact with the upper part of the inner surface of the boss portion of the orbiting scroll, and friction and heat generation occur. Therefore, it causes damage such as seizure of the rocking bearing.

  The present invention has been made in view of the above problems in the prior art, and an object of the present invention is to provide a scroll compressor capable of preventing the slider from lifting and preventing the swinging bearing from being damaged. To do.

A scroll compressor according to the present invention includes a container constituting an outer shell, a main shaft provided in the container and rotatably supported, and an orbiting scroll mounted on the main shaft eccentrically with respect to the central axis of the main shaft. And a fixed scroll that is fixed to the container and is opposed to the orbiting scroll and that forms a compression chamber for compressing fluid between the orbiting scroll and a lower surface of the orbiting scroll. A hollow cylindrical boss portion; a slider rotatably accommodated in the boss portion; and an eccentric shaft portion formed at an upper end of the main shaft and inserted into the slider, wherein the slider has two short side surfaces. a slit formed in a rectangular shape and having two long sides, of the two long sides of the slit, the side of the load side showing a side receiving a load generated in compressing the fluid It includes a stepped portion formed in the upper end of the side surface of the anti-load side showing the opposite side, of the two long sides of the slit, and a flat slider plate which is provided on a side surface of the load side and , the eccentric shaft portion, the upper end of the side surface corresponding to the side surface of the stepped portion of the slits are formed, have a protruding step which is formed so as to protrude, the radial dimension of the projecting step portion The diameter dimension of the eccentric shaft part is smaller than the dimension obtained by subtracting the diameter dimension of the eccentric shaft part from the diameter dimension of the slit, and the diameter dimension of the eccentric shaft part and the slider plate are different from the diameter dimension of the slit. It is larger than the dimension obtained by reducing the thickness direction .

  As described above, according to the present invention, a step portion is provided in the slit of the slider and a protruding step portion is provided in the eccentric shaft portion of the main shaft, thereby preventing the slider from being lifted and preventing the rocking bearing from being damaged. It becomes possible.

It is a figure which shows typically the cross section at the time of seeing an example of the scroll compressor which concerns on Embodiment 1 of this invention from the front. It is the schematic which shows an example of the slider provided in the scroll compressor of FIG. It is a figure which shows typically the principal part cross section at the time of seeing an example of the slider and eccentric shaft part in the scroll compressor of FIG. It is a figure which shows typically the principal part cross section at the time of seeing the other example of the slider and eccentric shaft part in the scroll compressor of FIG. 1 from the front. It is the schematic for demonstrating the dimension of each part of the slider of FIG. 3, and an eccentric shaft part. It is the schematic for demonstrating the dimension of the space between the slider, eccentric shaft part, and boss | hub part in the scroll compressor of FIG. It is a figure which shows typically the principal part cross section at the time of seeing an example of the slider and eccentric shaft part in the scroll compressor which concerns on Embodiment 2 of this invention from the front. It is the schematic which shows an example of the slider provided in the scroll compressor which concerns on Embodiment 2 of this invention. It is the schematic for demonstrating the dimension of each part of the slider of FIG. 7, and an eccentric shaft part.

Embodiment 1 FIG.
[Configuration of scroll compressor]
Hereinafter, the scroll compressor according to Embodiment 1 of the present invention will be described.
A scroll compressor is one of the components of a refrigeration cycle apparatus used in, for example, an air conditioner, a refrigeration apparatus, a refrigerator, a freezer, or a hot water supply apparatus, and a fluid such as a refrigerant circulating through the refrigeration cycle apparatus. Inhaled, compressed, and discharged as a high temperature and high pressure state.

FIG. 1 is a diagram schematically showing a cross section when an example of the scroll compressor 1 according to Embodiment 1 of the present invention is viewed from the front.
FIG. 2 is a schematic diagram showing an example of the slider 18 provided in the scroll compressor 1 of FIG.

As shown in FIG. 1, the scroll compressor 1 is comprised including the compression part 10 and the drive part 20 which were accommodated in the container 2 which comprises an outer shell.
The container 2 includes an intermediate container 2a that forms an intermediate part, a lower container 2b provided at the lower part of the intermediate container 2a, and an upper container 2c provided at the upper part of the intermediate container 2a. It has become.

A suction pipe 4 for sucking fluid such as refrigerant gas is connected to the intermediate container 2a.
The lower container 2b is an oil sump 3 for storing refrigerating machine oil that is lubricating oil.
A discharge pipe 5 for discharging a compressed fluid is connected to the upper container 2c.

  The compression unit 10 includes a fixed scroll 11, a swing scroll 12, and a frame 13 fixed to the intermediate container 2a.

  The fixed scroll 11 is for compressing a fluid together with a rocking scroll 12 to be described later, and is fixed to the frame 13 by a bolt or the like (not shown). The fixed scroll 11 is disposed so as to face the rocking scroll 12 and is disposed above the rocking scroll 12 when viewed from the front.

The fixed scroll 11 has a base plate 11a, a lap portion 11b, a seal 11c, and a discharge port 11d.
The base plate 11 a is formed in a flat plate shape substantially parallel to the horizontal plane, and a lap portion 11 b is erected on the lower surface facing the swing scroll 12.

The wrap part 11b is formed in a spiral projection. The wrap portion 11b is combined with a wrap portion 12b of the orbiting scroll 12, which will be described later, thereby forming a compression chamber 15 whose volume is relatively changed by the oscillation of the orbiting scroll 12.
A seal 11c is provided at the tip of the wrap portion 11b. This is to reduce fluid leakage from the tip of the wrap portion 11b when the fixed scroll 11 and the orbiting scroll 12 are disposed facing each other.

A discharge port 11d is provided at the center of the base plate 11a. The discharge port 11d is formed so as to penetrate the upper surface and the lower surface, and discharges a fluid such as a refrigerant gas compressed in the compression chamber 15 to a discharge space 6 provided in the upper portion of the fixed scroll 11. belongs to. In other words, the discharge port 11 d is formed in the vertical direction so as to communicate the compression chamber 15 and the discharge space 6.
The “central portion” of the base plate 11a refers to a central portion in the radial direction when the base plate 11a is viewed from above.

A discharge valve 19 that opens or closes the discharge port 11d is provided on the surface of the base plate 11a opposite to the surface facing the rocking scroll 12.
The discharge valve 19 closes the discharge port 11d and restricts the flow of fluid from the compression chamber 15 to the discharge space 6 when the pressure on the compression chamber 15 side is smaller than a preset pressure. The discharge valve 19 opens the discharge port 11d when the pressure on the compression chamber 15 side becomes equal to or higher than a preset pressure.

  The orbiting scroll 12 is provided to compress a fluid such as a refrigerant together with the fixed scroll 11. The orbiting scroll 12 is disposed to face the fixed scroll 11 and is disposed below the fixed scroll 11 when viewed from the front. Further, the orbiting scroll 12 is attached to the main shaft eccentrically with respect to a central axis of a main shaft 23 described later.

The orbiting scroll 12 has a base plate 12a, a wrap portion 12b, and a seal 12c.
The base plate 12 a is formed in a disk shape substantially parallel to the horizontal plane, and is provided so as to be supported by the frame 13. The base plate 12a performs a swinging motion by rotation of a main shaft 23 described later.
Between the base plate 12 a and the frame 13, a thrust plate 14 that supports the swing scroll 12 is provided. The base plate 12a and the thrust plate 14 are brought into close contact with each other through the lubricating oil, thereby constituting a thrust bearing.

A lap portion 12b is erected on the upper surface of the base plate 12a facing the fixed scroll 11.
The wrap portion 12 b is formed in a spiral projection having substantially the same shape as the wrap portion 11 b of the fixed scroll 11. The wrap portion 12 b forms a compression chamber 15 by being combined with the wrap portion 11 b of the fixed scroll 11. Thus, in the state where the wrap portion 11b and the wrap portion 12b are combined, the winding directions of the wrap portion 11b and the wrap portion 12b are reversed.
Similar to the wrap portion 11b of the fixed scroll 11, a seal 12c for reducing fluid leakage is provided at the tip of the wrap portion 12b.

A boss portion 17 is formed on the surface of the base plate 12a opposite to the surface facing the fixed scroll 11 (hereinafter referred to as “thrust surface” as appropriate).
The boss portion 17 is formed in a hollow cylindrical shape, and a slider 18 is rotatably accommodated therein. Although details will be described later, an eccentric shaft portion 23 a formed at the upper end of the main shaft 23 is inserted into the slit 18 a formed in the slider 18. And the rocking | fluctuation bearing is comprised because the inner peripheral part of the boss | hub part 17 and the outer peripheral part of the slider 18 closely_contact | adhere via lubricating oil.

An Oldham ring 16 is provided on the thrust surface of the base plate 12a.
The Oldham ring 16 is for preventing the orbiting scroll 12 from rotating and causing a revolving orbiting motion, that is, an orbiting motion.

  The frame 13 is fixed to the intermediate container 2a and slidably supports the swing scroll 12. A main shaft 13 is inserted in the central portion of the frame 13 in the radial direction, and a main bearing 13a that rotatably supports the main shaft 23 is formed.

The slider 18 is interposed between the inner peripheral surface of the boss portion 17 and the eccentric shaft portion 23a of the main shaft 23, and makes the swing radius of the swing scroll 12 variable.
As shown in FIG. 2, the slider 18 is formed in a disk shape, and a slit 18 a is formed in the central portion in the radial direction. The slit 18a is formed in a rectangular shape having two short side surfaces and two long side surfaces, and the eccentric shaft portion 23a of the main shaft 23 is inserted therein.
In the example shown in FIG. 2, the short side surface of the slit 18a is formed in an arc shape. The reason why the short side surface is formed in an arc shape in this way is, for example, to ensure the strength of the slider 18 while ensuring the movable range of the eccentric shaft portion 23a in the slit 18a.

The eccentric shaft portion 23a of the main shaft 23 has an arcuate side surface in one of the two side surfaces facing each other, the cross section of which is the same as that of the slit 18a so as to fit into the slit 18a. It is formed in a rectangular shape.
By forming the slit 18 a and the eccentric shaft portion 23 a in this way, the slider 18 can slide only in a certain direction on a plane perpendicular to the axial direction of the main shaft 23.

A slider plate 18b is provided on the side surface on the load side of the other side surface of the slit 18a of the slider 18.
Here, the “load side” refers to a side that receives a gas load generated when a fluid such as a refrigerant is compressed.
The detailed structure of the slider 18 and the eccentric shaft portion 23a will be described later.

The drive unit 20 includes a rotor 21, a stator 22, and a main shaft 23.
The rotor 21 is fixed to the main shaft 23 and is rotationally driven by energizing a stator 22 described later to rotate the main shaft 23.
The stator 22 is fixed to the intermediate container 2a, and is configured by winding a coil around a steel plate. Further, the steel plate of the stator 22 is provided with a notch (not shown), for example, so that a fluid such as refrigerant gas can flow through the notch.
The electric rotary machine 30 is configured by combining the rotor 21 and the stator 22.

The main shaft 23 transmits a driving force to the orbiting scroll 12 to perform an orbiting motion.
An eccentric shaft portion 23 a is formed at the upper end of the main shaft 23 and is inserted into a slit 18 a of the slider 18 provided inside the boss portion 17.
The upper side of the main shaft 23 is supported by the main bearing 13 a of the frame 13. A sleeve 24 is provided between the main shaft 23 and the main bearing 13a for smooth rotation of the main shaft 23.

The lower end of the main shaft 23 is rotatably supported by a ball bearing 32 press-fitted into a bearing housing portion 31a formed at the radial center of a subframe 31 provided at the lower portion of the intermediate container 2a.
An oil hole 23 c is formed inside the main shaft 23. The oil hole 23c is used to distribute the lubricating oil, and the lubricating oil stored in the oil sump 3 is supplied to each sliding portion by being sucked by the oil pump 33 described later through the oil hole 23c. Is done.

The subframe 31 is provided in the lower part of the intermediate container 2a. As described above, the sub-frame 31 has the bearing housing portion 31a. The subframe 31 is provided with a positive displacement oil pump 33.
The oil pump 33 is rotated by a pump shaft 23 b formed integrally with the main shaft 23, and sucks the lubricating oil stored in the oil sump 3.

[Structure of slider and eccentric shaft]
Next, the structure of the slider 18 and the eccentric shaft part 23a in the scroll compressor 1 according to the first embodiment will be described.
FIG. 3 is a diagram schematically showing a cross section of the main part when an example of the slider 18 and the eccentric shaft portion 23a in the scroll compressor 1 of FIG. 1 is viewed from the front.
FIG. 4 is a diagram schematically showing a cross section of the main part when another example of the slider 18 and the eccentric shaft portion 23a in the scroll compressor 1 of FIG. 1 is viewed from the front.

As shown in FIG. 3, the slider 18 is provided with a flat slider plate 18b on the side surface on the load side of the slit 18a.
In addition, a step portion 18c is formed along the entire side surface at the upper end of the side surface of the slit 18a opposite to the side surface on the load side (hereinafter referred to as “anti-load side” as appropriate).

The eccentric shaft portion 23a is formed with a protruding step portion 23d that protrudes along the entire side surface so as to correspond to the step portion 18c of the slider 18 at the upper end on the side opposite to the load when the eccentric shaft portion 23a is inserted into the slit 18a. .
Further, on the side surface of the eccentric shaft portion 23a that contacts the slider plate 18b on the load side, an arc-shaped crowning shape portion 23e that protrudes outward is formed.

  Thus, by forming the stepped portion 18c and the protruding stepped portion 23d, when the main shaft 23 is rotationally driven to lift the slider 18 and move upward along the axial direction, the stepped portion 18c of the slider 18 is eccentric. It interferes with the protruding step 23d of the shaft 23a. Therefore, the lift of the slider 18 can be restricted.

In the example shown in FIG. 3, the case where the crowning shape portion 23e is formed on the eccentric shaft portion 23a has been described. However, the present invention is not limited to this, and for example, as shown in FIG. 4, the crowning shape portion is formed on the eccentric shaft portion 23a. 23e may not be formed.
Thus, even when the crowning shape portion 23e is not formed, the lift of the slider 18 can be restricted.

[Dimensions of slider and eccentric shaft part]
Next, the relationship of the dimension of each part in the slider 18 and the eccentric shaft part 23a is demonstrated.
In the first embodiment, it is necessary to easily assemble the slider 18 and the eccentric shaft portion 23a, and to regulate the lifting of the slider 18 so that the orbiting scroll 12 operates normally. . Therefore, the dimensions and the like of each part in the slider 18 and the eccentric shaft part 23a are determined so as to satisfy these conditions.

FIG. 5 is a schematic diagram for explaining the dimensions of each part of the slider 18 and the eccentric shaft portion 23a of FIG.
FIG. 6 is a schematic diagram for explaining the size of the space between the slider 18, the eccentric shaft portion 23 a, and the boss portion 17 in the scroll compressor 1 of FIG. 1.

First, consider the case where the slider 18 and the eccentric shaft portion 23a are assembled.
In this case, for example, as shown in FIG. 5, after the eccentric shaft portion 23a of the main shaft 23 is inserted into the slit 18a of the slider 18 before the slider plate 18b is attached, the slider plate is placed on the load side surface of the slit 18a. Install 18b.
At this time, the radial dimension b of the protruding step portion 23d of the eccentric shaft portion 23a, the radial dimension c of the most convex portion of the crowning shape portion 23e in the eccentric shaft portion 23a, and the slider plate 18b before being attached. Between the diameter d of the slit 18a, it is necessary to satisfy the following formula (1).
[Equation 1]
b <dc (1)

Next, it will be considered that the lifting of the slider 18 is restricted.
In this case, when the slider 18 is lifted, the step portion 18c of the slider 18 needs to reliably interfere with the protruding step portion 23d of the eccentric shaft portion 23a.
Therefore, in order for the step portion 18c to interfere with the protruding step portion 23d, it is necessary to satisfy the following expression (2) between the dimension a in the thickness direction of the slider plate 18b and the dimensions b to d described above. There is.
[Equation 2]
b> d−c−a (2)

That is, based on the formula (1) and the formula (2), the relationship of the following formula (3) is established between the dimensions a to d of each part.
[Equation 3]
d−c>b> d−c−a (3)

Next, let us consider how the swing scroll 12 operates normally.
By determining the dimensions of each part of the slider 18 and the eccentric shaft part 23a to the dimensions as described above, the slider 18 can be prevented from rising, but the slider 18 is provided between the step part 18c and the protruding step part 23d. It will be slightly lifted by the clearance.
However, in order for the orbiting scroll 12 to operate normally, even when the slider 18 is lifted in this way, the upper surface of the slider 18 comes into contact with the inner surface upper portion 17a of the boss portion 17 of the orbiting scroll 12. It is necessary to prevent sliding.
Therefore, in order to prevent the slider 18 and the boss portion 17 from contacting each other, the dimension e of the space between the upper surface of the eccentric shaft portion 23a and the inner surface upper portion 17a of the boss portion 17, the step portion 18c and the protruding step portion 23d. It is necessary to satisfy the following formula (4) with the axial dimension f of the main shaft 23 between:
[Equation 4]
e> f (4)

  By determining the dimension e and the dimension f based on the formula (4), friction and heat generation caused by sliding of the upper surface of the eccentric shaft portion 23a and the inner surface upper portion 17a of the boss portion 17 can be prevented, and seizure of the rocking bearing can be achieved. Can be prevented.

  In this way, by determining the dimensions a to f of the respective portions in the slider 18, the eccentric shaft portion 23a, and the boss portion 17, the assembly can be easily performed without adding new parts to the main shaft 23. As a result, the lift of the slider 18 can be restricted, and the swing scroll 12 can operate normally.

  Note that the dimension a in the thickness direction of the slider plate 18b is preferably less than 1 mm, and more preferably 0.5 mm. In addition, the dimension b in the radial direction of the protruding step portion 23d is preferably less than 1 mm, for example. Furthermore, the dimensions c to f are preferably set in consideration of the strength when the scroll compressor 1 is actually used.

[Operation of scroll compressor]
Next, the operation of the scroll compressor 1 according to the first embodiment will be described.
In FIG. 1, when electric power is supplied to the electric rotary machine 30, a current flows through the coil of the stator 22 and a magnetic field is generated. The rotor 21 is rotated by this magnetic field, and the main shaft 23 supported by the main bearing 13a and the ball bearing 32 is rotationally driven. When the main shaft 23 is rotationally driven, the slider 18 is also rotated inside the boss portion 17 via the eccentric shaft portion 23a as the main shaft 23 is rotationally driven.
Then, the orbiting scroll 12 is controlled to rotate by the Oldham ring 16 and performs an orbiting motion. Thereby, the fluid such as the refrigerant gas sucked from the suction pipe 4 is compressed by the wrap portion 11b of the fixed scroll 11 and the wrap portion 12b of the swing scroll 12 through a suction port (not shown) of the frame 13. Flow into 15.

  The fluid that has flowed into the compression chamber 15 moves to the center of the orbiting scroll 12 by the orbiting motion of the orbiting scroll 12 and is compressed. At this time, the orbiting scroll 12 is subjected to a thrust load that tends to be separated in the axial direction by a fluid such as a refrigerant gas to be compressed, and this thrust load is supported by a thrust bearing constituted by the thrust plate 14.

The compressed fluid passes through the discharge port 11 d of the fixed scroll 11 and is discharged into the discharge space 6 against the discharge valve 19.
Then, the fluid discharged into the discharge space 6 is discharged from the container 2 to the outside through the discharge pipe 5.

  A part of the fluid sucked from the suction pipe 4 passes through the notch of the steel plate of the stator 22 and cools the lubricating oil stored in the electric rotary machine 30 and the oil sump 3.

  As described above, in the first embodiment, the step 18c is provided on the side opposite to the load of the slit 18a in the slider 18 and the projecting step 23d is provided on the eccentric shaft 23a of the main shaft 23. Can be prevented. Then, sliding due to contact between the eccentric shaft portion 23a of the main shaft 23 and the boss portion 17 of the swing scroll 12 can be prevented, and damage such as seizure of the swing bearing due to friction and heat generation can be prevented.

Embodiment 2. FIG.
Next, a scroll compressor according to Embodiment 2 of the present invention will be described.
The second embodiment is different from the first embodiment only in the position where the step portion 18c of the slit 18a in the slider 18 and the protruding step portion 23d of the eccentric shaft portion 23a in the main shaft 23 are provided.
In addition, the same code | symbol is attached | subjected to the part similar to the scroll compressor 1 which concerns on Embodiment 1, and detailed description is abbreviate | omitted.

[Structure of slider and eccentric shaft]
FIG. 7 is a diagram schematically showing a cross-section of the main part when an example of the slider 18 and the eccentric shaft portion 23a in the scroll compressor 1 according to Embodiment 2 of the present invention is viewed from the front.
FIG. 8 is a schematic diagram showing an example of the slider 18 provided in the scroll compressor 1 according to Embodiment 2 of the present invention.

As shown in FIGS. 7 and 8, the slider 18 is provided with a slider plate 18b on the side surface on the load side of the slit 18a.
Further, a step portion 18c is formed along the entire side surface at the upper end of the side surface on the load side of the slit 18a.

The eccentric shaft portion 23a is formed with a protruding step portion 23d that protrudes along the entire side surface so as to correspond to the step portion 18c of the slider 18 at the upper end on the load side in a state of being inserted into the slit 18a.
Similarly to the first embodiment, a crowning shape portion 23e is formed on the side surface on the load side that contacts the slider plate 18b of the eccentric shaft portion 23a.
In the second embodiment, as in the first embodiment, the crowning shape portion 23e may not be formed on the eccentric shaft portion 23a.

  Thus, by forming the stepped portion 18c and the protruding stepped portion 23d, when the main shaft 23 is rotationally driven and the slider 18 is lifted and moves upward along the axial direction, the stepped portion 18c of the slider 18 is eccentric. It interferes with the protruding step 23d of the shaft 23a. Therefore, the lift of the slider 18 can be restricted.

[Dimensions of slider and eccentric shaft part]
Next, the relationship of the dimension of each part in the slider 18 and the eccentric shaft part 23a is demonstrated.
Also in the second embodiment, as in the first embodiment, the slider 18 and the eccentric shaft portion 23a can be easily assembled, and the slider 18 is prevented from being lifted, so that the orbiting scroll 12 is properly operated. Need to work. Therefore, the dimensions and the like of each part in the slider 18 and the eccentric shaft part 23a are determined so as to satisfy these conditions.
In this example, the dimension e and the dimension f shown in FIG. 6 are the same as those in the first embodiment, and thus description thereof is omitted.

FIG. 9 is a schematic diagram for explaining the dimensions of each part of the slider 18 and the eccentric shaft part 23a of FIG.
First, consider the case where the slider 18 and the eccentric shaft portion 23a are assembled.
In this case, as shown in FIG. 9, when the scroll compressor 1 is operated, the dimension g in the protruding direction of the protruding step portion 23d of the eccentric shaft portion 23a, the side surface on the side opposite to the load of the slit 18a in the slider 18, and the It is necessary to satisfy the following formula (5) between the dimension h of the space between the side surfaces of the eccentric shaft portion 23a facing the side surface.
The dimension g indicates the dimension from the tip of the protruding step portion 23d to the same plane as the boundary surface between the slider 18 and the slider plate 18b.
[Equation 5]
g <h (5)

  Thus, by determining the dimension g and the dimension h, the eccentric shaft part 23a can be inserted into the slit 18a of the slider 18 before the slider plate 18b is attached. Therefore, the slider 18 and the eccentric shaft portion 23a can be easily assembled.

  The relationship between the dimension e of the space between the upper surface of the eccentric shaft part 23a and the inner surface upper part 17a of the boss part 17 and the dimension f of the clearance between the step part 18c and the protruding step part 23d is the same as that of the first embodiment. The same shall apply.

Here, the crowning shape portion 23e provided on the slider 18, the slider plate 18b, and the eccentric shaft portion 23a is in contact with each other because the load is always applied on the load side during the operation of the scroll compressor 1. Therefore, even when the dimension g of the protruding step portion 23d is small, the effect of preventing the slider 18 from being lifted can be sufficiently obtained.
Therefore, the dimension g of the protruding step portion 23d is preferably, for example, less than 1 mm, and more preferably 0.5 mm.

On the other hand, when the operation of the scroll compressor 1 is stopped, the slider 18, the slider plate 18b, and the crowning shape portion 23e are separated because they are not loaded. At this time, if the dimension h of the space between the eccentric shaft portion 23a and the slider 18 is large, the eccentric shaft portion 23a and the slider 18 may collide irregularly when the operation is started and when the operation is stopped.
Therefore, it is preferable that the dimension f of the space between the eccentric shaft portion 23a and the slider 18 is, for example, less than 1 mm.

  As described above, in the second embodiment, the step portion 18c is provided on the load side surface of the slit 18a in the slider 18, and the protruding step portion 23d is provided on the eccentric shaft portion 23a of the main shaft 23. Similarly, the slider 18 can be prevented from rising. Then, sliding due to contact between the eccentric shaft portion 23a of the main shaft 23 and the boss portion 17 of the swing scroll 12 can be prevented, and damage such as seizure of the swing bearing due to friction and heat generation can be prevented.

  DESCRIPTION OF SYMBOLS 1 Scroll compressor, 2 container, 2a Middle container, 2b Lower container, 2c Upper container, 3 Oil sump, 4 Suction pipe, 5 Discharge pipe, 6 Discharge space, 10 Compression part, 11 Fixed scroll, 11a Base plate, 11b Lapping part, 11c seal, 11d discharge port, 12 swing scroll, 12a base plate, 12b lapping part, 12c seal, 13 frame, 13a main bearing, 14 thrust plate, 15 compression chamber, 16 Oldham ring, 17 boss part, 17a Inner surface upper part, 18 slider, 18a slit, 18b slider plate, 18c stepped part, 19 discharge valve, 20 drive part, 21 rotor, 22 stator, 23 main shaft, 23a eccentric shaft part, 23b pump shaft, 23c oil hole, 23d protruding step Part, 23e crowning shape part, 24 sleeve, 30 Electric rotating machine, 31 subframe, 31a bearing housing, 32 ball bearing, 33 oil pump.

Claims (4)

A container constituting the outer shell,
A main shaft provided in the container and rotatably supported;
An orbiting scroll mounted on the main shaft eccentrically with respect to the central axis of the main shaft;
A fixed scroll that is fixed to the container and is provided opposite to the orbiting scroll, and forms a compression chamber for compressing fluid between the orbiting scroll;
A hollow cylindrical boss provided on the lower surface of the orbiting scroll;
A slider rotatably accommodated in the boss part;
An eccentric shaft portion formed at the upper end of the main shaft and inserted into the slider;
The slider is
A slit formed in a rectangular shape having two short sides and two long sides;
Of the two long side surfaces of the slit, a step portion formed at the upper end of the side surface on the opposite side to the side opposite to the load side indicating the side receiving the load generated when compressing the fluid;
Of the two long sides of the slit, a flat slider plate provided on the side of the load side,
The eccentric shaft portion is
At the upper end of the side surface corresponding to the side surface where the step portion in the slit is formed, has a protruding step portion formed to protrude,
The radial dimension of the protruding step part is smaller than the dimension obtained by subtracting the radial dimension of the eccentric shaft part from the radial dimension of the slit, and the radial dimension of the protruding step part is determined from the radial dimension of the slit. A scroll compressor that is larger than a diameter dimension of an eccentric shaft part and a dimension obtained by reducing the thickness direction of the slider plate. The scroll compressor according to claim 1, wherein a dimension between an upper surface of the eccentric shaft part and an upper part of an inner surface of the boss part is larger than an axial dimension of the main shaft between the step part and the protruding step part. The eccentric shaft portion is
3. The scroll compressor according to claim 1, further comprising an arcuate crowning shape portion protruding outward on a side surface of the load side. 4. A container constituting the outer shell,
A main shaft provided in the container and rotatably supported;
An orbiting scroll mounted on the main shaft eccentrically with respect to the central axis of the main shaft;
A fixed scroll that is fixed to the container and is opposed to the orbiting scroll, and forms a compression chamber for compressing fluid between the orbiting scroll;
A hollow cylindrical boss provided on the lower surface of the orbiting scroll;
A slider rotatably accommodated in the boss portion;
An eccentric shaft portion formed at the upper end of the main shaft and inserted into the slider;
The slider is
Slits,
A step portion formed on the side surface on the opposite side to the side opposite to the load side indicating the side receiving the load generated when compressing the fluid of the slit;
The eccentric shaft portion is
Have a protruding step which protrudes toward the side where the stepped portion in said slit,
The scroll compressor , wherein a radial dimension of the eccentric shaft part including the protruding step part is smaller than a radial dimension of the slit not including the step part .

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