JPH05126074A - Scroll compressor - Google Patents

Abstract

PURPOSE:To prevent the leakage of refrigerant through the sliding face of a bearing with no increase of sliding resistance due to sealing members, by providing a space connected through to an oil reservoir between a bearing of a frame and a scroll, and enclosing the sealing members in the space. CONSTITUTION:Between a main bearing 8 of a main frame 7 not shown in the figure and a driving shaft 17 of a first scroll 13 of a scroll compressor, a ring-shaped space 32 is constructed with a ring-shaped groove provided in the lower portion of the main frame 7 and a plate 34 closing the groove. In the ring-shaped space 32, a sealing ring member 35 is arranged. The space 32 is connected to an oil reservoir 2 through a connection hole 36. Where, the gap A between the inner peripheral surface of the sealing ring member 35 and the driving shaft 17 is specified to be smaller than the gap B between the main bearing 8 and the driving shaft 17. On the other hand, the gap C between the outer peripheral surface of the member 35 and the main bearing 8 is specified to be larger than the gap B.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor for rotating both scrolls in the same direction for compression.

[0002]

2. Description of the Related Art A conventional scroll compressor is constructed, for example, as disclosed in Japanese Patent Publication No. 1-35196. Here, a conventional example will be described with reference to this publication. In FIG. 7, the conventional example shown in this figure includes a housing 50, a discharge chamber 51, a first scroll 52 which is a drive scroll housed in the housing 50, and a second scroll which is a driven scroll. 53,
The rotary shaft 5 which is a drive shaft integrated with the first scroll 52.
4, a rotary shaft 55 that is a driven shaft integrated with the second scroll 53, an electric motor 56 that is a drive source of the first and second scrolls 52 and 53, and a slide ring 57 that forms a mirror plate 58 of the first scroll 52. The closed space 61 formed between the inner walls 60 of the first housing member 59 facing this and the sliding ring 62 between the end plate 63 of the second scroll 53 and the inner wall 65 of the second housing 64 facing this. It has a formed sealed space 66 and a lubricating system path.

As shown in FIG. 7, the housing 50 is constructed by combining first and second housing members 59 and 64. A gas inlet port 67 is formed on a side portion of the second housing 64, and an end cover 70 having an oil supply hole 69 is attached to an end portion of the tubular portion 68.

As shown in FIG. 7, the discharge chamber 51 is connected to a first housing member 59, and a gas discharge port 71 is formed at a side portion of the discharge chamber, and a cylindrical portion 72 is further provided. An end cover 73 is attached to the end of the.

The first scroll 52 has an end plate 58 and a wrap 74. On the other hand, the second scroll 53 includes an end plate 63, a wrap 75, and a peripheral edge portion 7 provided on the end plate 63.
6. The end plate 58 of the first scroll 52 has a flange 77 provided on the peripheral edge portion 76 so as to face the outer edge portion. The second scroll 53 is provided with a compression space 78 inside the peripheral edge portion 76, and the peripheral edge portion 76 has a gas inlet port 7.
9 is provided. The wraps 74 and 75 are formed in a spiral shape of an involute or a curve similar thereto, and are intermeshed with each other. The end plates 58, 63 are provided with gas passage holes 80, 81 for introducing gas pressure from the compression space 78 into the closed spaces 61, 66. Further, the Oldham coupling 82 is incorporated between the end plate 58 of the first scroll 52 and the flange 77 of the second scroll 53, and the second scroll 53 is driven as the first scroll 52 is driven. The second scroll 5 is driven in the same direction, and the second scroll 5 with respect to the first scroll 52.
3 is drivingly connected so as not to rotate.

The rotation shaft 54 of the first scroll 52 and the second
The centers 53 of the scroll 53 and the rotation shaft 55 of the scroll 53 are eccentrically attached to each other with an interval ε therebetween. The wrap 7 is provided on the half of the rotary shaft 54 of the first scroll 52 on the end plate 58 side.
A gas discharge port 83 is provided that communicates with the discharge chamber 51 from the compression space 78 formed between No. 4 and No. 75.
The rotating shaft 54 of the first scroll 52 is supported by a bearing 84 provided in the boss portion of the first housing member 59 and a bearing 85 provided in the cylindrical portion 72 of the discharge chamber 51, and the rotating shaft 54 in the axial direction is supported. It can rotate in a fixed position and is directly connected to the electric motor 56.

In the scroll compressor having this structure,
The second scrolls 52 and 53 are rotated in the same direction to compress the refrigerant in the compression space 78, and the first and second scrolls 5
The vibrations of the compression compressors 2, 53 during the compression operation are reduced so that the scroll compressor can be used for high speed.

[0008]

However, in the conventional scroll compressor, the closed space 61 is formed by the sliding ring 57 between the end plate 58 of the first scroll 52 and the inner wall of the first housing 59 that faces the end plate 58. And the sliding ring 62 supplies the refrigerant in the compression space 78 in the middle of compression to the end plate 63 of the second scroll 53 and the closed space 66 formed between the inner wall 65 of the second housing 64 facing the end plate 63. Since the rotating parts are sealed by the sliding rings 57 and 62 while pressing the back surfaces of the first scroll 52 and the second scroll 53, the relative rotation speed of the sealing parts is high, and the durability of the sliding rings is improved. There was a problem that the sealing property deteriorates.

The present invention solves the above problems,
An object of the present invention is to provide a scroll compressor that improves the sealability and durability of the seal member.

[0010]

SUMMARY OF THE INVENTION The present invention comprises an internal high-pressure closed container having an oil reservoir, an electric element and a scroll compression element housed in the container, and the scroll compression element is provided with a frame having a bearing. And a first scroll that is driven by an electric element with a spiral wrap and a shaft provided upright on the end plate, and a second scroll that has a spiral wrap and a shaft installed upright on the end plate. , The first scroll and the second scroll are assembled by interlocking the wraps with each other and eccentric the rotation center of the second scroll with respect to the rotation center of the first scroll. An Oldham coupling that rotates the scroll in the same direction as the first scroll, and forms a space communicating with a high-pressure oil reservoir between the frame bearing and the scroll. It is obtained by accommodating the rotatable seal member in this space.

According to the present invention, a space communicating with a high-pressure oil reservoir is formed between the bearing of the frame and the shaft of the scroll, and the space between the shaft and the shaft is formed in the space. A rotatable seal member that is smaller than the gap between the shaft and the shaft is housed.

According to the present invention, a space communicating with a high-pressure oil reservoir is formed between the frame bearing and the rotating portion of the scroll, and a space between the bearing and the shaft is formed in the space. The seal member is rotatable and has a size smaller than the gap between the bearing and the shaft.

[0013]

The present invention is constructed as described above,
A space communicating with a high-pressure oil reservoir is formed between the frame bearing and the scroll, and a rotatable seal member is housed in this space, and a seal surface between the seal member and the scroll and the bearing is provided. It is sealed with oil to reduce sliding resistance.

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the embodiments shown in FIGS.

Reference numeral 1 denotes a closed container having an oil reservoir 2 at the bottom thereof, in which an electric element 3 is housed on the upper side and a scroll compression element 4 is housed on the lower side. The electric element 3 is composed of a stator 5 and a rotor 6 arranged inside the stator.

Reference numeral 7 is a main frame, and a main bearing 8 is integrally provided at the center of the main frame. Reference numeral 9 denotes an auxiliary frame which is attached by pressure contact with the inner wall of the closed container 1, and the main bearing 8 of the main frame 7 and an eccentric auxiliary bearing 10 are attached to this auxiliary frame. The main frame and the auxiliary frame 9 are fixed by bolts 12 so as to form a hollow chamber 11 inside.

The scroll compression element 4 is composed of a first scroll 13 driven by the electric element 3 and a second scroll 14 which rotates in the same direction as the first scroll 13. The first scroll 13 includes a disk-shaped end plate 15, a spiral wrap 16 which is erected on one surface of the end plate and has a curved involute shape, and the end plate 1
The drive shaft 17 is inserted into and fixed to the rotor 5 so as to protrude to the center of the other surface of the rotor 5. The first scroll 13 constitutes a drive side scroll. Second
The scroll 14 includes a disk-shaped end plate 18, a spiral wrap 19 formed on one surface of the end plate and formed of an involute curve, and a driven shaft protruding in the center of the other surface of the end plate 18. It is composed of 20 and. And the second
The scroll 14 constitutes a driven scroll.

The first scroll 13 has a drive shaft 17 supported by a main bearing 8 of the main frame 7, and the second scroll 14
Has a driven shaft 20 supported by an auxiliary bearing 10 mounted on an auxiliary frame 9, and a wrap 1 for both scrolls 13 and 14.
A plurality of compression spaces 21 are formed inside the hollow chamber 11 by interlocking 6 and 19 with each other.

The drive shaft 17 is provided with a discharge hole 23 for discharging the refrigerant compressed in the compression space 21 to the upper space 22 of the electric element 2 in the closed container 1.

Reference numeral 24 is a restricting member for restricting the axial movement of the second scroll 14, and this restricting member comes into contact with the end plate 18 of the second scroll 14 and is fixed to the first scroll 13 with bolts 25. There is. Further, an annular wall 27 that holds the ball bearing 26 with the auxiliary frame 9 is provided so as to project from the restriction member 24. 28 is a regulating member 2
4 is a retaining ring of the ball bearing 26 attached to the annular wall of No. 4 of FIG.

Reference numeral 29 is an Oldham coupling provided between the first scroll 13 and the second scroll 14, and this Oldham coupling rotates the first scroll 13 and the second scroll 14 in the same direction. It swings relatively.

Reference numeral 30 denotes an annular refrigerant guide member attached to the outer periphery of the lower portion of the regulating member 24, and this guide member is the compression space 2
The suction port 31 that communicates the inside 1 with the inside of the hollow chamber 11 is covered.

Reference numeral 32 denotes an annular space formed between the main bearing 8 of the main frame 7 and the drive shaft 17 of the first scroll 13, and the annular space is an annular space provided below the main bearing 8 of the main frame 7. It is formed by a groove 33 and a plate 34 attached to the main frame 7 so as to close the annular groove.

A seal ring member 35 is provided in the annular space 32.
Is stored. The seal ring member is formed of a cylindrical metal having a substantially rectangular cross section. The gap A between the inner peripheral surface of the seal ring member 35 and the drive shaft 17 is smaller than the gap B between the main bearing 8 and the drive shaft 17, and the outer peripheral surface of the seal ring member 35 and the main bearing 8 are separated from each other. The gap C between them is formed larger than the gap B between the main bearing 8 and the drive shaft 17.

Reference numeral 36 is a communication hole formed in the main bearing 8, and this communication hole communicates the high pressure oil reservoir 2 in the closed container 1 in which the oil is stored with the upper end in the annular space 32.

37 is an auxiliary bearing 10 and a second scroll 1
4 is an annular space formed between the driven shaft 20 and the driven shaft 20, and the annular space is formed by an annular groove 38 provided in the lower portion of the auxiliary bearing 10. In the annular space 37, a seal ring member 39 made of a metal having a substantially rectangular cross section is housed. The seal ring member is held by a retaining protrusion 40 formed at the lower end of the auxiliary bearing 10 so as to protrude inward. The gap D between the inner peripheral surface of the seal ring member and the driven shaft 20 is smaller than the gap E between the auxiliary bearing 10 and the driven shaft 20, and the outer peripheral surface of the seal ring member 39 and the auxiliary bearing 10 are separated from each other. The gap F between them is formed larger than the gap E between the auxiliary bearing 10 and the driven shaft 20.

Sealing materials 41 and 42 having different sizes are sandwiched between the second scroll 14 and the regulating member 24. A passage 43 provided between the driven shaft 20 of the second scroll 14 and the end plate 18 which communicates with the oil reservoir 2 in the closed container 1 is opened between these seal members.

Reference numeral 44 is a suction pipe, which is a hollow chamber 11
There is an opening at the bottom inside. The opening of the suction pipe 44 faces the refrigerant guide member 30. Reference numeral 45 denotes a discharge pipe, which is provided above the closed container 1.

In the scroll compressor having such a structure, when the electric element 3 is rotated, its rotational force is transmitted to the first scroll 13 via the drive shaft 17. The rotational force transmitted to the first scroll is transmitted to the second scroll 14 via the Oldham's joint 29, and rotates the second scroll in the same direction as the first scroll 13. The second scroll 14 is driven by the driven shaft 20 with respect to the center of the drive shaft 17 of the first scroll 13.
Is rotated at a position where the center of is eccentric by an interval ε. Therefore, the first scroll 13 and the second scroll 14
Means that the compression space 21 formed by these scrolls is gradually reduced from the outside to the inside, flows into the hollow chamber 11 from the suction pipe 44, and is rotated.
The refrigerant that has flowed into the suction port 31 from the inside is compressed into the outside compression space 21. This compressed refrigerant is the first
Discharge hole 23 provided in the drive shaft 17 of the scroll 13
To discharge into the upper space 22 of the electric element 3 from the discharge pipe 4
5 is discharged from the closed container 1.

The seal ring member 35 housed in the annular space 32 formed by the annular groove 33 of the main bearing 8 and the plate 34 is pressed against the plate 34 by the oil flowing from the communication hole 36. In addition, the seal ring member 35
The gap A between the drive shaft 17 and the drive shaft 17 is made smaller than the gap B between the main bearing 8 and the drive shaft 17, so that the oil retaining force in the gap A can be increased. And
The high pressure portion in the closed container 1 and the low pressure portion of the hollow chamber 11 are sealed by the pressure contact surface between the seal ring member 35 and the plate 34 and the oil in the gap A between the seal ring member and the drive shaft 17, and the high pressure portion. The refrigerant is prevented from leaking to the low pressure portion via the main bearing 8.

The seal ring member 35 has an outer peripheral surface and the main bearing 8.
By making the clearance C between the drive shaft 17 and the clearance A larger than the clearance A, the drive shaft 17 is prevented from moving with the drive shaft 17 and coming into contact with the drive shaft 17 when the drive shaft 17 bends. Further, the seal ring member 35 is rotatably arranged on the drive shaft 17 through the oil, so that the sliding resistance in the gap A can be made the viscous resistance of the oil, and the sliding resistance can be reduced to increase the input. I try to keep it down.

The seal ring member 35 is a plate 34.
By changing the contact area of the surface pressed against, the sealing force can be adjusted and the speed at which the drive shaft 17 rotates can be changed.

Since the seal ring member 39 housed in the annular space 37 of the auxiliary bearing 10 is immersed in the oil of the oil sump 2, the upper end surface is pressed against the auxiliary bearing 10. The seal ring member 39 has a gap D between the driven shaft 20 and a gap E between the auxiliary bearing 10 and the driven shaft 20.
By making it smaller, the oil holding force in the gap D can be increased. The high-pressure portion in the closed container 1 and the low-pressure portion in the hollow portion 11 are sealed by the seal ring member 3
The pressure contact surface between 9 and the auxiliary bearing 10 and the oil in the gap D between the seal ring member and the driven shaft 20 prevent the refrigerant in the high pressure portion from leaking to the low pressure portion through the auxiliary bearing 10. There is.

By making the gap F between the outer peripheral surface and the auxiliary bearing 10 larger than the gap D, the seal ring member 39 moves together with the driven shaft 20 when the driven shaft 20 bends so that the driven shaft 20 does not contact. I am trying. Further, the seal ring member 39 is rotatably arranged on the driven shaft 20 through the oil, whereby the sliding resistance in the gap D is made to be the viscous resistance of the oil, and the sliding resistance is reduced to increase the input. I try to keep it down.

4 to 6 show a second embodiment of the present invention, in which the seal ring member 46 housed in the annular space 32 of the main bearing 8 flows into the annular space 32 from the communication hole 36. The high-pressure oil is brought into contact with the end plate 15 of the first scroll 13 to rotate with the scroll. The clearance C between the outer peripheral surface of the seal ring member 46 and the main bearing 8 is made smaller than the clearance B between the drive shaft 17 and the main bearing 8 to increase the oil retaining force in the clearance C. I am trying. The high-pressure portion in the closed container 1 and the low-pressure portion in the hollow chamber 11 are sealed by the seal ring member 46 and the end plate 15 of the first scroll 13.
And the oil in the gap C between the seal ring member and the main bearing 8 seals the refrigerant in the high pressure portion.
It is designed so that it does not leak to the low pressure part via the.

The seal ring member 47 arranged at the lower end of the driven shaft 20 of the second scroll 14 is pressed against the end surface of the driven shaft 20 by being immersed in the oil in the oil sump 2. Further, in the seal ring member 47, the gap F between the outer peripheral surface and the auxiliary bearing 10 is made smaller than the gap E between the auxiliary bearing 10 and the driven shaft 20, whereby the gap F is formed.
It is designed to increase the holding power of oil at. The high-pressure portion in the closed container 1 and the low-pressure portion of the hollow portion 11 are sealed by the pressure contact surface between the seal ring member 47 and the driven shaft 20 and the oil in the gap F between the seal ring member and the auxiliary bearing 10. The refrigerant in the high pressure portion is prevented from leaking to the low pressure portion via the auxiliary bearing 10.

The seal ring members 46 and 47 are the first and second
By making pressure contact with the rotating parts of the scrolls 13 and 14, the mounting structure is simpler than that of the embodiment shown in FIGS.

[0038]

As described above, according to the present invention, a space communicating with the high pressure oil reservoir is formed between the frame bearing and the scroll, and the rotatable seal member is housed in this space. Therefore, it is possible to prevent the refrigerant in the high pressure portion from leaking to the low pressure portion via the sliding surface of the bearing without causing an increase in sliding resistance due to the seal member.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a scroll compressor showing a first embodiment of the present invention.

FIG. 2 is an enlarged sectional view of an essential part of a seal ring member on the main frame side of the present invention.

FIG. 3 is an enlarged cross-sectional view of a main part of a seal ring member on the auxiliary frame side of the present invention.

FIG. 4 is a vertical sectional view of a scroll compressor showing a second embodiment of the present invention.

FIG. 5 is an enlarged cross-sectional view of the main part of the seal ring member on the main frame side of the present invention.

FIG. 6 is an enlarged sectional view of a main part of a seal ring member on the auxiliary frame side of the present invention.

FIG. 7 is a vertical sectional view showing a conventional scroll compressor.

[Explanation of symbols]

 1 Airtight Container 2 Oil Reservoir 3 Electric Element 4 Scroll Compression Element 7 Main Frame 8 Main Bearing 9 Auxiliary Frame 10 Auxiliary Bearing 11 Hollow Chamber 13 First Scroll 14 Second Scroll 15, 18 End Plate 16, 19 Wrap 17 Drive Shaft 20 Driven shaft 21 Compression space 29 Oldham coupling 32,37 Annular space 35,39 Seal ring member 36 Communication hole

Claims (3)

[Claims] 1. An internal high-pressure closed container having an oil reservoir, an electric element and a scroll compression element housed in the container, the scroll compression element having a frame having a bearing, and a spiral wrap on an end plate. A first scroll driven by an electric element by vertically arranging a shaft and a shaft, and a second scroll in which a spiral wrap and a shaft are erected on the end plate. The second scroll is assembled by engaging the wraps with each other so as to face each other and eccentric the rotation center of the second scroll with respect to the rotation center of the first scroll. In a scroll compressor having an Oldham coupling that rotates in the same direction, a space communicating with a high-pressure oil reservoir is formed between the frame bearing and the scroll. The scroll compressor is characterized in that a rotatable seal member is housed in this space. 2. An internal high-pressure closed container having an oil reservoir, an electric element and a scroll compression element housed in the container, the scroll compression element including a frame having a bearing, and a spiral wrap on an end plate. A first scroll driven by an electric element by vertically arranging a shaft and a shaft, and a second scroll in which a spiral wrap and a shaft are erected on the end plate. The second scroll is assembled by engaging the wraps with each other so as to face each other and eccentric the rotation center of the second scroll with respect to the rotation center of the first scroll. In a scroll compressor equipped with an Oldham coupling that rotates in the same direction, a space communicating with a high-pressure oil reservoir is formed between the frame bearing and the scroll shaft. And a rotatable seal member having a clearance between the shaft of the scroll and a bearing is smaller than the clearance between the bearing and the shaft. Characteristic scroll compressor. 3. An internal high pressure airtight container having an oil sump, an electric element and a scroll compression element housed in the container, the scroll compression element having a frame having a bearing, and a spiral wrap on an end plate. A first scroll driven by an electric element by vertically arranging a shaft and a shaft, and a second scroll in which a spiral wrap and a shaft are erected on the end plate. The second scroll is assembled by engaging the wraps with each other so as to face each other and eccentric the rotation center of the second scroll with respect to the rotation center of the first scroll. In a scroll compressor equipped with an Oldham coupling that rotates in the same direction, a space communicating between a high pressure oil reservoir between the bearing of the frame and the rotating portion of the scroll. And a rotatable seal member having a clearance between the bearing and the shaft smaller than the clearance between the shaft and the shaft of the scroll and the clearance between the bearing and the shaft. Scroll compressor characterized by.