JP3025154B2 - Shaft support structure - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a support structure for a shaft of a scroll compressor, for example.

[0002]

2. Description of the Related Art In general, in a scroll type compressor as a compressor, a fixed scroll member having a substrate and a spiral portion, and a movable scroll member having a substrate and a spiral portion are meshed with each other at the spiral portion. A compression chamber is formed between both scroll members. And
With the rotation of the shaft, the movable scroll member revolves around the axis of the fixed scroll member, whereby the compression chamber is moved from the outer peripheral side of the spiral part to the center side, and the gas is compressed.

FIG. 5 shows a conventional scroll compressor.
A shaft 72 connected to the movable scroll member 71 is supported by a front housing 74 via a bearing 73. A seal member 75 made of a rubber-based material for preventing leakage of lubricating oil and the like from between the front housing 74 and the shaft 72 is provided on the inner peripheral surface of the front housing 74.
Is installed. Further, a dam 77 is provided on the inner peripheral surface of the boss portion 76 of the front housing 74 for damping the lubricating oil leaked from between the seal member 75 and the shaft 72 due to deterioration of the seal member 75 or the like. Seal member 7
The axial movement of the dam 5 and the dam 77 is regulated by the C-ring 78.

Accordingly, in this compressor, the sealing member 75
Outside the front housing 74 (left side in the figure)
After that, the dam 77 and the C-ring 78 are assembled in this order. When inspecting and replacing the seal member 75, the seal member 75 is removed after the C ring 78 and the dam 77 are removed from the front housing 74.

FIG. 6 shows a scroll compressor having a structure different from that of the above-described scroll compressor. In this compressor structure, the shaft 85 is supported by the boss portion 82 of the front housing 81 and the bearings 83 and 84 press-fit into the front housing 81. A seal member 86 is provided on the inner peripheral surface of the front housing 81 between the bearings 83 and 84. The seal member 86 used in this compressor has a higher durability than the seal member 75 used in the compressor in FIG. Therefore, no dam is provided in this type of compressor.

In this compressor, unlike the compressor of FIG. 5, the seal member 86 is inserted from inside the front housing 81 (right side in FIG. 6). When checking and replacing the seal member 86, the front housing 8
Bolt (not shown) connecting 1 to rear housing 87
To remove the front housing 81 and the rear housing 87
Remove from Then, the bearing 84 is removed from the front housing 81 together with the shaft 85. Thereafter, the seal member 86 is removed from the front housing 81.

[0007]

However, each of the scroll compressors has the following problems. (1) In the compressor of FIG.
Is supported, the boss portion 76 becomes thicker, and the compressor becomes larger. In addition, since a C-ring 78 for regulating the movement of the seal member 75 and the dam 77 is required, there is a problem that the number of parts and the assembling work are large.

On the other hand, in the compressor shown in FIG.
Since the bearing 83 is supported on the inner periphery of the boss 2, the boss 82 becomes thicker, and the compressor becomes larger. (2) In the compressor shown in FIG. 6, when lubricating oil leaks from the seal member 86 to the boss portion 82 due to aging or the like, grease filled in the bearing 83 flows with the lubricating oil, and Burning or the like may occur.

(3) In the compressor shown in FIG.
From the width is small, contact touch area between the front housing 81 and the bearing 84 is small. Therefore, the bearing 84 is easily loosened with respect to the front housing 81. In order to prevent this rattling, a large press-fitting allowance (tightening allowance = 50 to 100 μm) is provided. Therefore, when inspecting and replacing the seal member 86,
Unless high heat (300 ° C. or more) is applied to the front housing 81, the bearing 84
Cannot be removed, adversely affecting the intrinsic properties of the front housing 81, the bearing 84, and the shaft 85, and lowering the hardness.

The present invention has been made to solve the above problems, and a first object of the present invention is to provide a shaft support structure capable of reducing the number of parts and reducing the diameter of a boss. .

[0011] The second purpose is to provide no dam or the like,
An object of the present invention is to provide a shaft support structure capable of damping lubricating oil.

[0012]

[0013]

[MEANS FOR SOLVING THE PROBLEMS] To achieve the above object
According to the first aspect of the present invention, the seal member is housed in a housing recess formed on an inner end surface of the second housing so as to open toward the first housing side, and the rolling bearing is provided in the second housing. Attached to the housing, the boss and the front
On the inner peripheral surface of the second housing between the housing recess.
Has an annular groove smaller in diameter than the outer diameter of the seal member.
At the same time, an oil outlet hole communicating with the annular groove and the outside is formed.
The gist is that it is provided in the second housing .

[0014] In the invention of claim 2, wherein the rolling bearing, as its gist the rolling elements are interposed between the outer ring and the inner ring is double row form ball bearing which is a plurality of rows arranged.

In the invention of claim 3, the rolling bearing is characterized in that the rolling element sandwiched between the outer ring and the inner ring is a roller bearing composed of a roller .

[0016]

[0017] In the invention 請 Motomeko 4, as its gist to move to integrally axially by the locking means and the rolling bearing and the shaft.

[0018]

[0019]

[0020]

[0021]

SUMMARY OF] According to the present invention, the movable scroll member is rotated in a housing chamber which is sealed by a sealing member in accordance with rotation of the shaft, the compression operation is performed. Therefore, the pressure inside the storage chamber is higher than outside the housing (outside air),
The seal member is pressed outward from the accommodation room. However, since the seal member is housed in the housing recess formed on the inner end surface of the second housing, even when pressed outward from the housing chamber, the seal member contacts the end surface of the housing recess and its movement is regulated. You. Therefore, there is no need for a member that restricts the movement of the seal member. Also, due to aging deterioration of seal members, etc.
Lubricating oil in the chamber leaks from between the shaft and seal member
However, the lubricating oil is blocked in the annular groove,
Since it is led to the outside through the hole, the boss side
No flow.

According to the second aspect of the present invention, since the double-row type ball bearing has a large width, the contact area with the second housing and the shaft is large. Thereby, the bearing is fixed to the second housing in a stable state. In addition, since the bearing has a plurality of rolling elements, the shaft can be stably rotated without providing the bearing on the boss portion side.

According to the third aspect of the present invention, the width of the roller bearing can be increased only by increasing the length of the roller and the outer ring (the inner ring may be included). Thus, the width of the bearing can be increased without arranging a plurality of rollers and without increasing the outer diameter of the bearing. By using the roller bearing having a large width, the contact area between the second housing and the shaft can be increased. Thereby, the bearing is fixed to the second housing in a stable state.

[0024]

[0025]

[0026]

[0027]

According to the fourth aspect of the present invention, the rolling bearing and the shaft are integrally moved in the axial direction by the engaging means. Thus, the shaft and the bearing can be simultaneously pulled out of the second housing during maintenance of the seal member, so that work efficiency is improved.

[0029]

[0030]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. As shown in FIG. 1, a front housing 1 as a second housing is connected and fixed to a front surface (a left side surface in FIG. 1) of a fixed scroll member 2 also serving as a center housing by a bolt (not shown). In this embodiment, the space formed by the front housing 1 and the fixed scroll member 2 is used as the accommodation room. The rear housing 3 is connected and fixed to the rear surface of the fixed scroll member 1 by bolts (not shown). In this embodiment, a first housing is formed by the fixed scroll member 2 and the rear housing 3. The shaft 4 is rotatably supported in the front housing 1 by a main bearing 5 as a rolling bearing, and an eccentric shaft 6 protrudes from an inner end thereof. The bush 7 is rotatably supported by the eccentric shaft 6, and a bearing 8 is fitted on the outer periphery thereof.

The movable scroll member 9 is rotatably supported by the bush 7 by fitting a fitting portion 10 on the front surface of the movable scroll member 9 to the bearing 8. The rotation is regulated. When the shaft 4 is rotated, the movable scroll member 9 includes the bush 7 and the bearing 8 by the eccentric shaft 6.
, Around the axis of the shaft 4.

The fixed scroll member 2 has a substrate 12 and a spiral portion 13 integrally formed on the inner surface thereof. Similarly, the movable scroll member 9 also includes a substrate 14 and a spiral portion 15 integrally formed on the inner surface of the substrate 14. And
The scroll members 2, 9 are engaged with each other at the spiral portions 13, 15, and the axial end faces of the spiral portions 13, 15 are opposed to the substrates 12, 14 of the opposed scroll members 2, 9.
Is facing.

The suction chamber 16 is formed between the outer peripheral portions of the spiral portions 13 and 15 of the opposed scroll members 2 and 9, and a refrigerant gas is sucked into the inside thereof. The compression chamber 17 is formed between the spiral portions 13 and 15 of the scroll members 2 and 9. The discharge hole 18 is formed at the center of the substrate 12 of the fixed scroll member 2, and connects the compression chamber 17 to a discharge chamber 19 in the rear housing 3. The discharge valve 20 is disposed at the outer end of the discharge hole 18, and the open position thereof is regulated by a retainer 21.

The boss portion 22 is provided to project from the front end surface of the front housing 1. The hole diameter of the boss 22 is larger than the outer diameter of the shaft 4, and the front end of the shaft 4 is inserted through the boss 22. The rotating plate 23 is spline-coupled to the shaft 4 in the boss portion 22. The pulley 24 is rotatably supported on the outer periphery of the boss portion 22 and is connected to a crankshaft (both not shown) of the engine via a V-belt. A clutch (not shown) is interposed between the rotary plate 23 and the pulley 24. With this clutch, the rotational force of the engine is transmitted from the pulley 24 to the shaft 4 via the rotary plate 23.

The housing recess 25 is provided in the front housing 1.
Is formed on the inner end face of the. The seal member 26 is housed in the housing recess 25. The movement of the seal member 26 toward the tip end of the shaft 4 is regulated by the end surface of the housing recess 25.

An oil storage groove 34 as an annular groove is formed on the inner peripheral surface of the front housing 1 between the storage recess 25 and the boss 22. The oil drain hole 35 is formed in the front housing 1 and communicates the oil storage groove 34 with the outside.

The main bearing 5 supporting the shaft 4 is a double row fixed type radial ball bearing in which two rows of balls 39 as rolling elements are arranged between an inner ring 37 and an outer ring 38. Therefore, the axial width of the main bearing 5 is larger than the width of the bearing 84 in FIG. The large-diameter portion 40 of the shaft 4 is inserted into the inner ring 37 of the main bearing 5, and the two are engaged with each other by a retaining ring 41 formed of a C-ring as locking means. The movement of the shaft 4 in the axial direction with respect to the main bearing 5 is restricted by the retaining ring 41. The outer ring 38 of the main bearing 5 is press-fitted into the inner wall of the front housing 1 (the outer ring 38 and the front housing 1 are tightly fitted). In this embodiment, the interference between the outer ring 38 and the front housing 1 is 20 to 60 μm. The restricting member 42 made of a C-ring is supported by the front housing 1 and prevents the main bearing 5 from coming off the front housing 1 by contacting the rear end surface of the outer ring 38 of the main bearing 5.

Next, the operation of the scroll type compressor will be described. When the rotating plate 23 is rotated via the pulley 24 with the driving of the engine, the rotational force is applied to the shaft 4.
Is transmitted to When the shaft 4 is rotated, the movable scroll member 9 revolves around the axis of the shaft 4 due to the eccentric rotation of the eccentric shaft 6. Thereby, the refrigerant gas is taken into the compression chamber 17 between the scroll members 2 and 9 from the suction chamber 16. Then, as the orbiting scroll member 9 revolves, the compression chamber 17 is moved from the outer peripheral side of the spiral portions 13 and 15 to the center side to gradually reduce the volume to perform a compressing action. Accordingly, the refrigerant gas is gradually compressed in the compression chamber 17, and is pushed to open the discharge valve 20 from the discharge hole 18 and discharged to the discharge chamber 19.

The refrigerant gas taken into the suction chamber 16 contains lubricating oil for lubricating each sliding portion. Leakage of lubricating oil from between the front housing 1 and the shaft 4 is prevented by the seal member 26. When the compressor is driven, the pressure inside the housings 1 and 2 is higher than the pressure outside the housing (outside air). Due to the pressure difference between the inside of the housings 1 and 2 and the outside air, the seal member 26 is pressed outward. However, the sealing member 26 is
5 and its movement is restricted by contacting the end face of the fifth member.

When the sealing performance of the seal member 26 deteriorates due to aging or the like, and the lubricating oil leaks to the boss portion 22 side, the lubricating oil is blocked by the oil accommodating groove 34. Then, the lubricating oil caught in the oil accommodating groove 34 drops out of the oil drain hole 35 to the outside.

Next, the operation when performing the maintenance work (replacement work or inspection work) of the seal member 25 will be described. First, the rotating plate 23 is attached to the boss 22 from the shaft 4.
The pulleys 24 are respectively removed from the. Next, the front housing 1 is removed from the fixed scroll member 2 by removing a bolt (not shown). After the eccentric shaft 6 is pulled out of the bush 7, the regulating member 42 is removed from the front housing 1.
Remove.

Next, the front housing 1 is heated. The heating temperature at this time is 100 to 150 ° C. Thereby, the interference fit between the front housing 1 and the main bearing 5 is released. In this state, the main bearing 5 is pulled from the front housing 1 with the eccentric shaft 6 (or the shaft 4 is pushed in from the boss 22 side). At this time, since the shaft 4 and the main bearing 5 are engaged via the retaining ring 41, the shaft 4 and the main bearing 5 are integrally pulled out of the front housing 1. Thereby, the sealing member 2
6 is exposed, and the seal member 26 can be removed from the accommodation recess 25. The assembling work process after the replacement or inspection of the seal member 26 is an operation opposite to that at the time of removing the seal member 26, and thus the detailed description is omitted here.

As described above, in the present embodiment, the following effects can be obtained by configuring the scroll compressor. (1) One double row fixed type bearing in which balls 39 are arranged in two rows
This was used to support the shaft 4. Thereby, the contact area between the front housing 1 and the outer ring 38 of the main bearing 5 can be increased, and the main bearing 5 can be fixed to the front housing 1 in a stable state. As a result, unlike the related art, it is not necessary to provide a bearing on the boss portion 22 side, and the number of components can be reduced.

Further, since the contact area between the front housing 1 and the main bearing 5 is increased, the main bearing 5 can be securely fixed to the front housing 1 even if the interference between them is reduced. As a result, it is possible to pull out the main bearing 5 from the front housing 1 even if the heating temperature of the front housing 1 is lowered, and it is possible to reduce adverse effects on the intrinsic properties of the front housing 1, the main bearing 5 and the shaft 4.

(2) The oil receiving groove 3 is formed on the inner peripheral surface of the front housing 1 between the recess 25 and the boss 22.
4 was formed. Thereby, even if the lubricating oil in the housings 1 and 2 leaks from between the shaft 4 and the seal member 26, the lubricating oil can be dammed without using parts such as dams. Slip with the rotating plate 23 can be prevented. As a result, the number of components can be reduced, and it is not necessary to provide a bearing between the boss portion 22 and the shaft 4, so that the outer diameter of the boss portion 22 can be reduced.

(3) Since the main bearing 5 and the shaft 4 are engaged with each other by the retaining ring 41, the shaft 4 and the main bearing 5 can be simultaneously pulled out from the second housing, and the efficiency of maintenance work can be improved. .

(4) The movement of the main bearing 5 in the axial direction with respect to the front housing 1 is regulated by the regulating member 42. Thereby, even if the interference between the front housing 1 and the main bearing 5 is reduced, the movement of the main bearing 5 with respect to the front housing 1 in the axial direction can be reliably prevented.

It should be noted that the present invention is not limited to the above-described embodiment, and may be configured as follows without departing from the spirit of the invention. (1) As shown in FIG.
A jig locking piece 45 whose tip is bent toward the axial center side is integrally formed on the end face 8. In this case, the main bearing 5
And the shaft 4 are not engaged by the retaining ring 41.
When pulling out the main bearing 5 from the front housing 1, after heating the front housing 1, a dedicated jig (not shown) is hooked on the jig locking piece 45. Then, in this state, the jig is pulled, first, only the main bearing 5 is pulled, and then, the shaft 4 is pulled out.
At this time, since the pulling force acts only on the outer ring 38 as compared with the case where the main bearing 5 is pulled out simultaneously with the shaft 4, the load applied to the ball 39 and the inner ring 37 is small.

(2) In the above embodiment, the locking means is C
The shaft 4 and the main bearing 5 can be integrally pulled out from the front housing 1 using a retaining ring 41 formed of a ring. Instead,
As shown in FIG. 3, a flange portion 47 may be formed on the end face of the large diameter portion 40 of the shaft 4, and may be used instead of the retaining ring 41. In the case of this configuration, when the main bearing 5 is pulled out, the eccentric shaft 6 is pulled (or the shaft 4 is connected to the boss portion 22).
By pushing the inner bearing 37 from the side of the boss 22, the main bearing 5 and the shaft 4 can be simultaneously pulled out of the front housing 1.

(3) In the above embodiment, the present invention is embodied by the support structure of the shaft 4 in the scroll type compressor, but the support structure of the shaft in the swash plate type compressor and the support structure of the crankshaft in the internal combustion engine. The present invention may be embodied.

(4) In the above embodiment, the double-row fixed type bearing is used as the main bearing 5, but this configuration may be embodied instead of the roller bearing as shown in FIG. The roller bearing includes a roller 50 and an outer ring 51 as rolling elements.
The width can be increased simply by increasing the length (which may include the inner ring). In this manner, the width of the rollers 50 can be increased without arranging a plurality of the rollers 50 and without increasing the outer diameter of the main bearing 5. Thus, in addition to the effects of the above-described embodiment, the size and weight of the front housing 1 can be reduced.

Other technical ideas grasped by the above embodiments will be described below together with their effects. (1) The shaft support structure according to claim 10, wherein the locking means is a flange portion formed integrally with the shaft.

When removing the bearing from the second housing, the flange is engaged with the end face of the rolling bearing by pulling (or pushing ) the shaft, and the rolling bearing is pressed by the flange. This makes it possible to remove the bearing rolling shaft simultaneously from the second housing.

[0054]

As described above in detail, according to the first aspect of the present invention, a member for restricting the movement of the seal member is not required, so that the number of parts is reduced and the assembling work is facilitated. Also,
Without dams, etc.
Lubricating oil in the storage chamber from the space between the shaft and the seal member
Even if leakage occurs, lubricating oil can be prevented from flowing to the boss.
You.

According to the second aspect of the present invention, since the rolling bearing is a double-row ball bearing, the shaft can be smoothly rotated without providing a plurality of bearings.

According to the third aspect of the present invention, since the rolling bearing is a roller bearing, the width of the bearing can be increased without arranging a plurality of rolling elements and without increasing the outer diameter of the bearing. Thus, the bearing is fixed to the second housing in a stable state, and thus the shaft can be smoothly rotated.

[0057]

[0058]

[0059]

[0060]

According to the invention of claim 4 , work efficiency such as maintenance of the seal member can be improved.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a scroll compressor according to one embodiment of the present invention.

FIG. 2 is a partial sectional view of a scroll compressor showing another example.

FIG. 3 is a partial sectional view of a scroll compressor showing another example.

FIG. 4 is a partial sectional view of a scroll type compressor showing another example.

FIG. 5 is a sectional view of a conventional scroll compressor.

FIG. 6 is a cross-sectional view of a conventional scroll compressor.

[Explanation of symbols]

1. Front housing as second housing, 2
... fixed scroll member constituting first housing, 3
... fixed scroll member constituting first housing, 4
... shaft, 5 ... main bearing as a rolling bearing, 12 ... a substrate of a fixed scroll member, 13 ... a spiral portion of a fixed scroll member, 14 ... a substrate of a movable scroll member, 15 ... a spiral portion of a movable scroll member, 37 ...
Reference numeral 38 denotes an outer ring, 39 denotes a ball as a rolling element, 41 denotes a retaining ring as a locking means, 42 denotes a C-ring as a regulating member, 45 denotes a jig locking piece, and 47 denotes a flange portion as a locking means. ... Rollers as rolling elements, 51 ... Outer ring

──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Tetsuhiko Fukanuma 2-1-1 Toyota-cho, Kariya-shi, Aichi Pref. Inside Toyota Industries Corporation (72) Inventor Tsuyoshi Takemoto 1-1-1, Showa-cho, Kariya-shi, Aichi Japan Japan Denso Co., Ltd. (72) Inventor Shigeru Hisaga 1-1-1, Showa-cho, Kariya-shi, Aichi Japan Denso Co., Ltd. (56) References JP-A-6-173866 (JP, A) A) Japanese Utility Model Hei 6-86216 (JP, U) Japanese Utility Model Hei 6-167284 (JP, U) Japanese Utility Model Hei 5-89882 (JP, U) Japanese Utility Model 58-37984 (JP, U) Japanese Utility Model Sho 58 -97321 (JP, U) JP 2-9109 (JP, Y2) US Patent 5,290,161 (US, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F04C 23/00-29/10 331 F04C 18/02 311 F16C 19/00-19/56 F16C 33/30-33/66

Claims (4)

(57) [Claims] A first housing having a substrate and a spiral portion; a movable scroll member having a spiral portion and a substrate meshing with the spiral portion of the first housing; and a movable scroll member connected to the first housing. A second housing that restricts axial movement of the second housing; a boss protruding from an outer end surface of the second housing; and a second housing that is supported via a rolling bearing, and one end of which is movable. A shaft connected to a scroll member, the other end of which is inserted through the boss portion; and a seal member interposed between the second housing and the shaft, for sealing the inside of the housing. The compression chamber is moved from the outer peripheral wall of the spiral part to the center side by applying the revolving scroll member around the axis of the first housing. In the scroll compressor, the seal member is housed in a housing recess formed in an inner end surface of the second housing so as to open toward the first housing side, and the rolling bearing is provided with 2 between the boss and the housing recess.
On the inner peripheral surface of the second housing, the outer diameter of the seal member
A small-diameter annular groove is also formed, and
Oil holes are provided in the second housing to communicate with
Shaft support structure that is. 2. The shaft support structure according to claim 1, wherein said rolling bearing is a double row ball bearing in which a plurality of rolling elements sandwiched between an outer ring and an inner ring are arranged. 3. The shaft support structure according to claim 1, wherein the rolling bearing is a roller bearing in which a rolling element sandwiched between an outer ring and an inner ring is formed of a roller. 4. The supporting structure of the shaft according to any one of claims 1 to 3 which moves integrally in the axial direction by the locking means and the rolling bearing and the shaft.