JPS62162778A - Gas compressor - Google Patents

Abstract

PURPOSE:To make pressure imposed on a driven shaft lower to produce a gas compressor being less in mechanical wear and high in reliability by forming the gas compressor in a rotary cylinder block type, and holding a driven shaft to which the said cylinder block has been fixed by a side plate through a bearing. CONSTITUTION:A side plate 3 is fixed to the open end plane of an approximately cup-shaped casing 1, and a driving shaft 5 having a helical bevel gear 4 fitted on it is inserted in the side of the casing 1. The one end of a driven shaft 16 to which a cylinder block 12 is fixed is engaged with the helical bevel gear 4 in inclination to it, and the other end of the drive shaft 16 is rotatably supported by a side plate 3 through a bearing 17. Pressure acting on the bearing 17 is therefore dispersed on its whole circumference to make the said pressure lower as compared with that in the case of a fixed shaft.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a gas compressor, and particularly to a gas compressor suitable for being mounted on an automobile.

[Conventional technology]

In a conventional fluid machine, a piston device is converted into reciprocating motion by swinging a swinging disk, as described in Japanese Patent Laid-Open No. 58-91383. However, no consideration was given to increasing the volumetric efficiency on the discharge side by using a rotating cylinder block.

[Problem that the invention seeks to solve]

The above conventional technology uses a rotating cylinder block,
No consideration was given to increasing the volumetric efficiency on the discharge side, and there were structural problems.

On the other hand, hydraulic pumps that rotate cylinder blocks are widely known, but there is no mention of their use in gas compressors.

An object of the present invention is to provide a highly reliable gas compressor that suppresses the pressure applied to the driven shaft, causing less mechanical wear.

[Means for solving problems]

The above object includes a drive shaft supported by a first outer casing, a rotary plate provided at the rear end of the drive shaft, a cylinder block arranged rotatably around the rotary plate, and a rotary plate provided at the rear end of the drive shaft. a piston device disposed in the through hole; a driven shaft fixed integrally with the cylinder block and having one end facing the rear end of the drive shaft with an inclination; a second outer casing which is joined to the other end of the driven shaft and rotatably supports the other end of the driven shaft;
This is achieved by holding it in the outer casing.

[Effect]

Since the driven shaft 16 held in the recess 3A of the side plate 3 via the bearing 17 is in a constantly rotating state, the load (pressure) on the bearing 17 is distributed over the entire circumference and is approximately half that of a fixed shaft. decreases to

〔Example〕

The present invention will be explained below based on embodiments shown in the drawings. 1st
The figure shows a sectional view of the main parts of the near compressor. In the figure, a side plate 3, which is a second outer casing, is arranged on the radial end surface of a casing 1, which is a first outer casing, and which is approximately bowl-shaped, with an O-ring 2 interposed therebetween. It is tightened and fixed with the assembly screw. A drive shaft 5 having a helical bevel gear 4 fitted at its tip is inserted into the center of the casing 1 and is held by the casing 1 via a radial bearing 6. Furthermore, a mechanical seal mechanism 8 is provided between the cylindrical portion IA of the casing 1 and the rotating shaft 5 and is prevented from being removed by a clip 7.

Further, inside the casing 1, a working chamber assembly 9 and a motion converting mechanism section 10 are housed. Here, the working chamber assembly 9 has a plurality of through holes 11 provided at equal intervals, a cylinder block 12 made of a light alloy such as an aluminum alloy, a piston portion 13 fitted in the through holes 11, Rod part 1
3A and a piston device 15 having a steel ball 14. A recess 3A is formed in the inner wall surface of the side plate 3, and a driven shaft 16 arranged at an angle of 20 degrees with respect to the drive shaft 5 is implanted on the outer periphery via a bearing 17. The driven shaft 16 has a helical bevel gear 18 formed on the outer periphery of its tip surface and meshes with the helical bevel gear 4 . Further, the driven shaft 16 has the cylinder block 12 fitted on its outer periphery, and a spherical bearing 19 fitted and fixed at the center of its tip, which is in contact with a hemispherical body 5A fixed at the center of the tip of the drive shaft 5. There is. The inner wall surface of the side plate 3 has an arc-shaped low-pressure passage 3B communicating with the suction port (not shown), and an arc-shaped high-pressure passage 3D formed opposite to the passage and communicating with the discharge port 3C.
A seal ring 20 made of a rubber material or the like is embedded around the high pressure passage to form a high pressure chamber. The seal ring can be more easily buried in this high pressure chamber by setting it somewhat lower than the inner wall surface. Further, the seal ring does not need to be provided with a positive step, but if a step is provided, it may be formed on the end face of the float valve, which will be described later. Reference numeral 21 denotes a flow valve constituting the cylinder head, which is an iron plate formed in a horseshoe shape as shown in FIG. 2, and is disposed between the side plate 3 and the cylinder block 12. This float valve has a high pressure side passage and a low pressure side passage connected to the side plate 3, respectively.
It is provided so as to face each of the passages formed in the same manner. The outer periphery thereof is arranged with a gap between it and the inner periphery of the casing, and is arranged concentrically with the driven shaft 16.

Note that since the float valve itself only needs to be substantially located on the high pressure side, it is formed by cutting out a horseshoe shape slightly larger than the area of the seal ring 20, but it may also be formed into a disk shape. Next, on the outer periphery of the drive shaft 5 corresponding to the outer periphery of the gear 4, a rotating plate 23 whose back surface is supported on the casing 1 by a thrust bearing 22 is fixed. This rotary plate 23 is made of aluminum alloy, etc., and as shown in FIG. A part of the plastically fluidized material is caused to flow into the annular groove 5B that has been formed in advance, and the two are mechanically connected by the tension force generated around the annular groove. On the other hand, the steel plate 14 of the piston fitting fi 15 is rotatably inserted into the concave surface 23A of the outer circumferential portion, and is supported so as to be prevented from being pulled out by the crimping force of the opening periphery 23B.

Note that the connection between the steel ball 14 and the rod portion 13A is also performed by plastic deformation of the rod member, as described above. Furthermore, the piston portion 13 and the rod portion 13A are made of aluminum and integrally molded to achieve weight reduction.

Furthermore, the high pressure passage (high pressure chamber) 3D of the side plate 3 and the spherical bearing 19
The through hole L9A provided therebetween communicates via a passage 3E provided in the side plate and a passage 16A provided in the driven shaft 16 to form an oil supply hole. A bushing 24 is arranged between the driven shaft 16 and the bottom surface of the recess in the side plate 3 to buffer thrust force and distribute lubricating oil.

In the above configuration, when the drive shaft 5 is rotated by the internal combustion engine, for example, the rotary plate 23 is also rotated.

This rotation simultaneously rotates the driven shaft 16 via the helical bevel gears 4A and 18A, and the cylinder block 12 is also rotated.

When the cylinder block 12 and the rotary plate 23 synchronize and rotate 1, for example to the left, the piston 15 near the inflow start end of the low pressure side passage 3B is moved to a position slightly closer to the bottom dead center than the top dead center. be.

As the cylinder block 12 rotates, the piston device 15 moves toward the bottom dead center and the low pressure side passage 3
Near the inflow end end of B, the piston 15 is at a position slightly closer to the top dead center than the bottom dead center.

Here, the piston device! 15 is at the bottom dead center, the cylinder penetration line 11 is connected to the low pressure side passage 3B and the high pressure side passage 3.
It is located in a position that does not overlap with both D.

When the cylinder block 11 further rotates and moves, the piston 15 moves toward the top dead center from near the outflow start end of the high pressure side passage 3D, and near the outflow end end, the piston 15 moves slightly closer to the bottom dead center than the top dead center. in position. Of course, here too, when the piston 15 is at the top dead center, the through hole 11 of the cylinder is in a position that does not overlap with both the low pressure side passage 3B and the high pressure side passage 3D. Next, when the high pressure side passage 3D becomes high pressure, the seal ring 20 creates a high pressure between the inner wall surface of the cylinder pro corner 12 and the float valve 21, so the float valve 21 is pressed against the end face of the cylinder block 12, and the through hole 11 Close the lid airtight with your own knife.

Therefore, the float valve 21 is always pressed toward the cylinder block by its own blade while the high pressure gauge is at high pressure, and airtightness with the cylinder block is always maintained in a stable state. Further, as described above, since the blade is self-bladed, there is no need to provide a separate suppressing means, and the blade is extremely simple, highly reliable, and has excellent productivity.

In addition, if only the high pressure side is a float valve, it can be made of a different material from the cylinder head, which is advantageous when considering weight reduction and further improves sealing performance. Normally, the operating state of the compressor is to mix and compress refrigerant and lubricating oil, so at the same time as a high pressure chamber is formed, lubricating oil flows through passages 3E-16A and 19A to the spherical bearing 19.
refuel. Moreover, the oil spouted from the bushing 4 also lubricates the bearing 17, and the self-cutting blade maintains smooth lubrication.

Since this oil supply path is formed inside using the components of the main body, it is not complicated and has an extremely good appearance.

Next, referring to FIG. 5, a description will be given of how the driven shaft 16 having a fixed cylinder block is extended to the side plate 3 and is rotatably held via a bearing 17.

First, the moment balance at the center of the hemispherical state 5A is Po: Discharge pressure (Kgf) Qo: Bore pitch (mm) (Note) Expressed in radius P5: Stress applied to the bearing (Kgf) Ql: Hemispherical body Distance from the center to the bearing center (mid) θ; Think of it as the direction (degrees) of the resultant force acting on the hemispherical body.

Po-no=Pt・fix.

Therefore, the stress P1 applied to the bearing is n.

P+=-PO.

l where n t= 70nv, Pox= 627 K
Assuming gfno=35mm, =313.5Kgf Also, the direction of the resultant force (θ) is =26.6'.

Therefore, compared to a case where a fixed shaft is provided on the side plate and the cylinder block is rotatably held there via a bearing, the stress PI applied to the bearing is reduced by 50%, and θ is reduced by 40%.

As shown in the above example, the force related to the bearing and the stress related to the hemispherical state are greatly reduced, resulting in a rotary cylinder block compressor with less mechanical wear and a long life. It becomes possible to

〔Effect of the invention〕

As described above, according to the present invention, since the driven shaft is rotatably held in the second outer casing, the pressure applied to the driven shaft can be kept small.
A highly reliable gas compressor with low mechanical wear is provided.

[Brief explanation of drawings]

Fig. 1 is a longitudinal sectional front view of the main parts of a car compressor according to an embodiment of the present invention, Fig. 2 is a front view of the same float valve, Fig. 3 is an m-om-m sectional view of Fig. 2, and Fig. 4 is FIG. 1 is an enlarged view of the main part, FIG. 5 is a vector diagram of the driven shaft in the present invention,
FIG. 6 is a vector diagram of FIG. 5. DESCRIPTION OF SYMBOLS 1... First outer casing, 3... Second outer casing, 5... Drive shaft, 12... Cylinder block, 16... Driven shaft, 17... Ned 23A 23e)

Claims (1)

[Claims] 1. A piston device disposed in a through hole of a cylinder block that rotates in accordance with rotation of a drive shaft, and gas flowing into and out of the through hole by reciprocating motion of the piston device. A gas compressor includes a drive shaft supported by a first outer casing, a rotary plate provided at the rear end of the drive shaft, and a cylinder block rotatably disposed around the rotary plate. a piston device disposed in the through hole of the first drive shaft; a driven shaft fixed integrally with the cylinder block and having one end facing the rear end of the drive shaft with an inclination;
and a second outer casing that is airtightly joined to the outer casing and rotatably supports the other end of the driven shaft. 2. In claim 1, the driven shaft is:
A gas compressor characterized in that the gas compressor is rotatably supported via a bearing in a recess formed on an inner side surface of a second outer casing. 3. Claim 1 or 2, characterized in that one end of the driven shaft is in contact with a hemispherical fixed shaft fixed to the rear end of the drive shaft via a spherical bearing. gas compressor. 4. A gas compressor according to claim 3, wherein the driven shaft is provided with an oil supply passage connecting the spherical bearing and the high pressure passage.