JPS61160501A - Fluid machine - Google Patents

Abstract

PURPOSE:To make it possible to obtain a high degree of mechanical efficiency with a simple structure, by obtaining discharge force or torque from the reciprocating motion of a piston disposed in a through-hole which is formed in a cylinder block rotated in association with the rotation of a journalled drive shaft. CONSTITUTION:In an air-compressor, when a drive shaft 5 is rotated, a rotary disc 23 is rotated by means of a gear cylinder 4. This rotation rotates a driven shaft 18 through helical bevel gears 4A, 18A so that a cylinder block 12 is also rotated. When the cylinder block 12 and the rotary dick 23 are rotated in synchronization with each other, a piston 15 positioned in the vicinity of a low pressure side passage 3B moves toward its bottom dead center while a piston positioned in the vicinity of a high pressure side passage 3D is moved toward its top dead center. When the pressure of the high pressured side passage 3D becomes high, a float valve 21 is pressed against the end face of the cylinder block 12 so that a through-hole 11 is hermetically closed by itself.

Description

[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a fluid machine, and particularly to a mechanism suitable for an air compressor or a hydraulic pump that obtains discharge pressure by pumping a working fluid such as gas or oil. This invention relates to a fluid machine equipped with.

[Background of the invention]

Generally, a liquid pump that pumps a working liquid such as oil or a liquid motor that obtains rotational force by using the head energy of the working liquid is well known as a fluid machine.

As a liquid machine of this kind, Japanese Patent Application Laid-Open No. 58-91
As typified by Figure 1 of Publication No. 383, a swash plate has a swash plate fixed to a drive shaft, and the rotation of the swash plate causes a swinging disk supported by the other shaft to swing, thereby performing reciprocating motion. In the rotary type, as shown in Figure 2 of the same publication, an oblique shaft is integrally provided at the output end of the drive shaft, and the eccentric movement of the oblique shaft is prevented from rotating through a rotation prevention means provided on the outer periphery of the oblique shaft. There is an oblique shaft rotation type that performs reciprocating motion by transmitting information to a supported rocking disk.

However, since the former transmits the rotation of the swash plate to the oscillating disk and converts it into reciprocating motion, an extra bearing means such as a needle bearing is required between the two, making the structure extremely complicated.

Furthermore, since the entire thrust load is received by the central pole bearing that holds the oscillating disk, frictional resistance is large and mechanical efficiency is extremely poor.

Further, since a piston device that connects to a piston slidably fitted in a cylinder is connected to the outer peripheral end of the oscillating disk, there is a restriction that the oscillating disk must not rotate. This rotation is prevented by meshing spur teeth on the side surface of the oscillating disk with a fixed bevel gear (so-called gear sliding type), which is not durable.

Next, the latter has an oblique shaft integrated with the drive shaft, and a rocking disk is provided on the outer periphery of the oblique shaft via a thrust bearing.
Like the former, there are problems with the thrust load being applied in the axial direction, the durability of the rotation preventing portion of the rocking disk, and the increased use of thrust bearings, and the structure is extremely complicated.

Furthermore, the oblique shaft was long and heavy, resulting in poor rotational balance during rotation, which was a major cause of vibration and noise. This rotational balance can also be said in the former example, but although it is corrected with balance weights, it cannot be balanced due to the shape, so it does not solve the fundamental unbalance, and it can cause vibrations. It appears.

This center runout acts on the drive shaft as an eccentric load, leading to shaft friction. Furthermore, mechanical vibration shortens the life of the machine, has no reliability as a product, and generates noise that causes discomfort to the user, so it must be eliminated.

Typical fluid machines have been explained above, but in all cases, the axial thrust load and the eccentric load on the drive shaft are large, and although many countermeasures have been taken, it is necessary to eliminate mechanical friction in the axial direction and drive the drive shaft. The eccentricity of the shaft was far from being eliminated, and the overall mechanical efficiency was extremely poor.

On the other hand, hydraulic pumps that rotate the cylinder block are also known, but a seat valve member is fixed to the high pressure chamber side of the side plate forming the outer casing, and the end face of the cylinder block is slid onto this seat valve member. Because they are being moved, the discharge force depends on the machining accuracy9 and assembly precision of both, and it is difficult to maintain airtightness between the two, resulting in a decrease in the discharge force and, ultimately, a decrease in pump efficiency. It had an impact.

[Purpose of the invention]

An object of the present invention is to provide a fluid machine with high mechanical efficiency by utilizing the structure.

[Summary of the invention]

The present invention includes a substantially cup-shaped casing that supports a drive shaft and forms an outer casing, a side plate that airtightly closes the open end of the casing, and a driven shaft that is rotationally opposed to the inner surface of the side plate. ,
a cylinder block that is located on the outer periphery of the drive shaft and rotates together with the driven shaft; and a float valve that is disposed between the end face of the cylinder block and the side plate and is pressed against the cylinder block by the discharge pressure of the high pressure chamber. a rotating plate fixed along the inner wall surface of the casing and around the outer periphery of the drive shaft; and a piston device having one end disposed in the through hole of the cylinder block and the other end locked to the rotating plate. It is a fluid machine consisting of.

[Embodiments of the invention]

The present invention will be explained below based on the embodiments shown in the figures. 1st
The figure shows a sectional view of the main part of the near compressor, and Fig. 2 shows an enlarged view of the main part. In the figure, a side plate 3 is disposed on the open end surface of a substantially bowl-shaped casing l via an O-ring 2, and is fastened to the casing 1 with several assembly screws. A drive shaft 5 is inserted into the center of the casing 1 and has a gear cylinder 4 fitted with four curved bevel gears at its tip, and the gear cylinder 4 is held in the casing 1 via a t-1t 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.

A working chamber assembly 9 and a motion conversion mechanism section 10 are housed inside the casing 1. 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 13
A and a piston device 15 having a steel ball 14.

A fixed shaft 16 is installed on the inner wall surface of the side plate 3 and is arranged at an angle of 20 degrees with respect to the drive shaft 5.

A cylindrical driven shaft 18 is attached to the outer periphery of the fixed shaft 16 via a bearing 17 and has a helical bevel gear 18A at its tip that meshes with the four helical bevel gears. The cylinder block 12 is fitted on the outer periphery of the driven shaft 18, and the inner periphery has a spherical tip surface integrally formed with the drive shaft 5 or a spherical bearing formed separately to receive intervening balls. 19 is fitted and fixed. The inner wall surface of the side plate 3 is formed with an arc-shaped low-pressure passage 3B that communicates with the suction port 3A, and an arc-shaped high-pressure passage 3D that is formed opposite to the passage and communicates with the discharge port 3C. A seal ring 20 made of a rubber material or the like is buried around the periphery to form a high pressure chamber. This high pressure chamber can be easily formed by setting it somewhat lower than the inner wall surface, and can be formed by burying the seal ring 20, so there is no need to actively create a step. However, if a step is to be provided, it may be formed on the end face of the float valve, which will be described later. Reference numeral 21 denotes a float valve constituting the cylinder head, which is a donut-shaped iron plate and is arranged between the side plate 3 and the cylinder block 12. This float valve is provided with a high-pressure side passage and a low-pressure side passage so as to face the respective passages formed in the side plate 3. The outer periphery thereof is arranged with a gap from the inner periphery of the casing, and is arranged concentrically with the fixed shaft 16. Note that the float valve itself only needs to be on the high pressure side, so cut it out in an arc shape that is slightly larger than the area of the seal ring 2.
It is preferable that the other iron plates other than the cut-out portion be fixedly arranged on the casing 1.

A rotating plate 23 whose back surface is supported on the casing 1 by a thrust bearing 22 is fixed to the outer periphery of the gear cylinder 4 on the drive shaft 5 side. This rotary plate 23 is made of aluminum alloy, etc.
As shown in FIG. 2, after fitting the center part into the gear cylinder 4,
The area near the center of the rotating plate is locally pressed vertically, and a part of the material that has plastically flowed at right angles is caused to flow into four previously formed annular grooves, which are then mechanically connected by the tension generated around the annular grooves. are doing. On the other hand, a piston device 1 is provided on the concave surface 23A on the outer periphery.
A steel ball 14 of No. 5 is rotatably inserted, and is supported so as to be prevented from being pulled out by the crimping force around the opening 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 part 13 and the rod part 13A are made of aluminum and integrally molded to realize weight reduction.

Furthermore, the high pressure passage (high pressure chamber) 3D of the side plate 3 and the spherical bearing 19
The 19 through holes provided in between are communicated via a passage 3E provided in the side plate and a passage 16A provided in the fixed shaft to form an oil supply hole.

A bushing 24 is arranged between the fixed shaft 16 and the spherical bearing 19 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 rotated via the gear cylinder 4. This rotation simultaneously rotates the driven shaft 18 via the helical bevel gears 4A and 18A, causing the cylinder block 12 to rotate.
Also rotate.

When the cylinder block 12 and the rotary plate 23 are synchronized in this way and rotate counterclockwise, for example, the piston 15 near the inflow start end of the low pressure side passage 3B moves from the top dead center to a position slightly toward the bottom dead center. It is in.

As the cylinder block 12 rotates, the piston 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, when the piston device 15 is at the bottom dead center, the through hole 11 of the cylinder is connected to the low pressure side passage 3B and the high pressure side passage 3B.
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, the piston 15 is slightly closer to the bottom dead center than the top dead center. It is located at Of course, here too, when the piston 15 is at the top dead center [6], 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 pressure between the inner wall surface of the cylinder block 12 and the float valve 21 becomes high due to the seal ring 20, so the float valve 21 is pressed against the end surface of the cylinder block 12, and the through hole 11 Close the lid airtight.

Therefore, while the high pressure side passage 3D is under high pressure, the float valve 21 is always pressed toward the cylinder block side by its own blade.
Airtightness with the cylinder block is always maintained in a stable state. Furthermore, as described above, since the blade is self-bladed, there is no need to provide a separate pressing means, and the blade is extremely simple, highly reliable, and has excellent productivity.

In addition, if the float valve is used only on the high pressure side, 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 a high pressure chamber is formed, lubricating oil flows through passages 3E-16A and 19A to spherical bearing 19.
refuel. Further, the oil spouted from the bushier 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.

Furthermore, since the rotary plate 23 is disposed on the drive shaft 5 side, the load on the bevel gear in the driving state is small, and operation can be performed with a small driving force. Furthermore, by molding the piston and rod parts from light metals such as aluminum, it is possible to create a piston device with low inertial energy, reducing weight and greatly extending the life of the piston seal. becomes possible. In other words, a compact and high-performance compressor can be realized.

Note that although this explanation focuses on a compressor, a hydraulic pump or one that converts linear motion into rotational motion may also be used.

〔Effect of the invention〕

According to the present invention, it is an object of the present invention to provide a fluid machine with a simple structure and high mechanical efficiency.

[Brief explanation of drawings]

The drawings show one embodiment of the fluid machine of the present invention, and FIG. 1 is a half-longitudinal sectional view of a compressor, and FIG. 2 is an enlarged view of the main part of FIG. 1. 1... Casing, 3... Side plate, 5... Drive shaft,
3D... High pressure passage (high pressure chamber), 15... Piston device, 12... Cylinder block, 18... Driven shaft, 21... 7o-) 14A, 18A... Bevel gear.

Claims (1)

[Claims] 1. A fluid machine in which a piston is disposed in a through hole of a cylinder block that rotates in accordance with the rotation of a drive shaft supported on the shaft, and a discharge force or rotational force is obtained by the reciprocating motion of the piston. There is a substantially bowl-shaped casing that supports the drive shaft and forms an outer casing, a side plate that airtightly closes the open end of the casing, and a drive shaft that is rotatably supported at an angle on the inner surface of the side plate. , a driven shaft whose outer periphery is abutted to the drive shaft at the center of its tip and meshes with the outer periphery via a bevel gear; a cylinder block located on the outer periphery of the drive shaft and rotates integrally with the driven shaft; and an end face of the cylinder block. and a float valve disposed between the side plates and pressed against the cylinder block by the discharge pressure of the high pressure chamber; a rotary plate fixed to the outer periphery of the drive shaft along the inner wall surface of the casing; and a piston device disposed in a through hole of the cylinder block, the other end of which is locked to the rotary plate. 2. A fluid machine according to claim 1, wherein the driven shaft is provided with an oil supply path connecting a high pressure chamber and a drive shaft abutting portion. 3. The fluid according to claim 1, wherein the piston and the rod are integrally molded from a light metal material, and a steel ball is plastically connected to the tip of the rod by a part of the plastically deformed rod material. machine. 4. In claim 1, the rotary plate is made of a light metal and is fitted around the outer periphery of the drive shaft, and is plastically deformed into a gear cylinder that forms a bevel gear at the tip and rotates integrally with the drive shaft. A fluid machine characterized by being plastically connected in some parts. 5. A fluid machine according to claim 1, wherein the bevel gear is a helical gear.