JPS6165081A - Fluid machine - Google Patents

Abstract

PURPOSE:To obtain a fluid machine equipping a high accurate valve mechanism of good air-tightness with simplified construction, by pressing a float valve with the pressure in a high pressure chamber being utilized and closing the through hole of a cylinder block to be covered by this float valve. CONSTITUTION:The opening end surface of a casing 1 is closed by a side plate 3 through an O ring 2. A float valve 30 is arranged in a part between this side plate 3 and a cylinder block 12. A part between said side plate 3 and the float valve 30 forms a high pressure chamber 29 communicating with a high pressure passage 3D by a seal ring 28. A fluid machine is constituted such that the pressure in said high pressure chamber 29 presses the float valve 20 to a side of the cylinder block 12.

Description

[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a fluid machine, and is suitable for a near compressor or a hydraulic pump that obtains discharge pressure by pumping a working fluid such as gas or oil to 1%. It relates to a fluid machine equipped with a mechanism.

[Background of the invention]

2. Description of the Related Art In general, a liquid pump that pumps a working liquid such as oil or a liquid motor that obtains rotational force by utilizing the head energy of the working liquid is well known as a fluid machine.

And, as this woodcutter's fluid machine, 1%
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 ball bearing that holds the oscillating disk, frictional resistance is large and mechanical efficiency is extremely poor.

Further, since the outer peripheral end of the oscillating disk is connected to a piston rod that connects to a piston that is slidably fitted into the cylinder, 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), and is not permanent.

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, the thrust load is applied in the axial direction, and there are problems with the durability of the rotation preventing portion of the oscillating 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 also a major factor in noise during shooting and M. This rotational balance can be said to be the same in the former example, but although the balance weight (5) is corrected, it does not solve the fundamental unbalance because it cannot be balanced due to the shape, and it does not lead to vibration. It appears.

This center runout acts on the drive shaft as an eccentric load, leading to shaft friction. Also, mechanical vibration shortens machine life.)
There is no reliability as a product at all.

This creates noise that causes discomfort to users and must be removed.

Typical fluid machines have been explained above, but in all cases the axial thrust load and the eccentric load applied to the drive shaft are large, and although many countermeasures have been taken to eliminate mechanical friction in the axial direction, The eccentricity 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 that forms the outer casing, and the end face of the cylinder block is slid onto this seat valve member. Because the pump is moving, the discharge force depends on the machining accuracy and assembly accuracy of both, and it is difficult to maintain an airtight space between the two, which reduces the discharge force and has a significant impact on pump efficiency.

[Purpose of the invention]

An object of the present invention is to provide a fluid machine having a simple structure and a highly accurate valve mechanism.

[Summary of the invention]

The present invention provides a through hole in a cylinder block that is in a fixed relationship with a rotary shaft supported by a shaft, and a float that is disposed between the crown and the end face of the cylinder block and is suppressed by the end face of the cylinder block using the pressure of a high pressure chamber. A fluid machine whose lid is closed by a valve.

According to the fluid machine configured in this way, the cylinder block and the motion conversion mechanism rotate in synchronization, so the cylinder block and the motion conversion mechanism appear to be stationary and round, and the piston makes reciprocating motion. A pump or compressor function is performed to perform this.

Furthermore, since the float valve is constantly pressed against the end face of the cylinder block by the high pressure generated by the self-cutting blade, it becomes a highly airtight valve mechanism.

[Implementation sequence of the invention]

The present invention will be explained below based on examples. Figure 1 shows the R1 cross section of the main part of the air congressor, Figure 2 shows the Kff-U cross section, and the
The figure shows an It-In sectional view.

In the figure, a side plate 3 is disposed on the open end surface of a substantially bowl-shaped casing 1 via an OIJ song, and is fastened and fixed to the casing 1 by several assembly screws 4. A rotating shaft 5 is inserted through the center of the side plate 3 and is held by the side plate 3 via a radial bearing 6. Moreover, a mechanical seal mechanism 8 is provided between the side plate 3 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 includes a cylinder block 12 having a plurality of through holes 11 provided at equal intervals, and a rod portion 1 fitted in the through holes 11.
3 and a piston 15 having a spherical portion 14, and a central hollow portion is press-fitted and fixed to one end of the rotating shaft 1. Here, fixing is not limited to press-fitting, and any mechanical connection can be used.

Reference numeral 16 denotes a thrust bearing that is arranged concentrically with the rotating shaft l and receives loads in the axial direction of the rotating shaft l and the cylinder block 12. On the other hand, a stepped hole 17 is formed at the center end of the cylinder block 12, and one moving shaft 18A of a cross-spike-shaped universal joint 18 is fitted into the stepped hole via a buffer spring 19. The tip faces the tip of the rotating shaft l with a spacer 20 interposed therebetween.

The drive 1II11 pongee 18A is locked via a key 21 so as to be movable only in the thrust direction.

One end of the driven shaft 22 of the universal joint 18 is
A fixed shaft 23 installed at an angle on the inner bottom surface of the casing l
It is supported on the outer periphery of the radial bearing 24 via a radial bearing 24. A pair of arms 22 are integrated with the driven shaft 22.
A is connected to a pair of arms 18B that are integral with the drive shaft 18A via a cross spider 25 formed in a cross shape. Note that it is better for the work to incline the fixed shaft 23 by preparing a necessary amount of inclined surface in advance on the inner bottom surface of the casing 1 and installing the fixed shaft 23 perpendicularly on the inclined surface.

Further, to explain the motion conversion mechanism 10, a disk-shaped rotary plate 26 has its center fixed to the outer periphery of the drive shaft 22, and the spherical portion 14 of the piston 15 is attached to the inner end surface of the outer periphery.
is held rotatably.

A thrust bearing 27 is disposed between the inner bottom surface of the casing and the back surface of the rotary plate 26 and receives the moving load of the piston 15.

Next, the valve mechanism will be explained. As can be seen from FIG. 2, the inner wall surface of the side plate 3 has an arc-shaped low-pressure passage 3B communicating with the suction port 3A, and an arc-shaped high-pressure passage 3D formed opposite to the passage and communicating with the discharge port 3C. A seal ring 28 made of rubber material or the like is buried around the high pressure passage.
A high pressure chamber 29 is formed. This high pressure chamber can be formed more easily if it is set somewhat lower than the inner wall surface as shown in the first cross section. This high pressure chamber 29 is connected to the seal ring 2
8 can be formed by burying it, so there is no need to proactively provide a step.

If a step is provided, it may be formed on the end face of the float valve, which will be described later. Reference numeral 30 denotes a float valve constituting the cylinder head, which is a donut-shaped iron plate and is disposed between the side plate 3 and the cylinder block 12. As shown in FIG. 3, this float valve has a high pressure side passage 30A1 and a low pressure side passage 3.
0B are provided so as to face respective passages formed in the side plate 3. The outer periphery thereof is arranged concentrically with the rotating shaft 5 with a slight gap between it and the inner periphery of the casing. Incidentally, since the float valve itself only needs to be substantially located on the high pressure side, it may be cut out in an arc shape larger than the area of the seal ring 2, and other iron plates may be fixedly arranged on the casing l.

In the above configuration, when the shaft 5 is rotated by, for example, an internal combustion engine, the cylinder block 12 is rotated in synchronization with the rotating shaft 5. In parallel with this, the driving side of the universal joint 18, the cross spider 25, and the driven side are also rotated at the same time.

The rotating plate 26 is also rotated at the same time.

When the cylinder block 12 and the rotating plate 26 synchronize in this way and rotate counterclockwise (for example, in FIG. 2), the low pressure side passage 3B
The piston 15 near the inflow start end is at a position slightly moved toward the bottom dead center from the top dead center. As the cylinder block 12 rotates counterclockwise and moves, the piston 15 moves toward the bottom dead center, and near the inflow end end of the low pressure side passage 3B, the piston 15 is located at a position slightly closer to the top dead center than the bottom dead center. .

Here, when the piston 15 is at the bottom 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. Furthermore, cylinder block 1
1 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 at a position slightly closer to the bottom dead center than the top dead center. . 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 28 creates a high pressure between the inner wall surface of the cylinder block 3 and the float valve 30.
2 and closes the through hole 11 airtightly with its own blade.

Therefore, while the high pressure side passage 3D is under high pressure, the float valve 30 is always pushed toward the cylinder block side by its own blade.
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 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.

FIG. 4 shows another embodiment to which the present invention is applied, and is characterized in that a bevel gear is used for the universal joint 180 in FIG. 1. A cylinder block 12 is press-fitted onto the outer periphery of the distal end of the rotating shaft 5, and a tube body 40 having a heavy shaft 40A is press-fitted onto the distal end. A second ball holder is connected to this tube body 40 via a buffer spring 41.
is inserted. 43 is a tube body 43 having a bevel gear 43A that meshes with the bevel gear 40A, and is provided with a ball holder 44. The two ball holders have spherical surfaces on their central end faces and face each other with the ball 45 in between.

And aluminum-silicon alloy is used to improve bearing function.

The coupling mechanism of this structure is constructed using a heavy mechanism so that the piston 15 can reciprocate by rotating the rotary plate 26. The other structures and operations are the same as those of the previous embodiment, and will therefore be omitted.

FIGS. 5 and 6 show still another embodiment of a hydraulic pump. Since the basic structure is the same as that in FIG. 1, a different float valve mechanism will be explained.

A stepped groove 53 is formed around a high-pressure side passage 52 that communicates with a discharge port 51 provided in a side plate (front cover) 50, and the bottom surface of this stepped groove 53 is, for example, a surface wider than the cross-sectional width of the seal ring 54. It becomes.

On the other hand, a float valve 55 in contact with the cylinder block 12
is formed into an arcuate shape with a convex cross section, and is fitted into the stepped *53. In this state, the cross-sectional width of the tip of the float valve 55 is wider than the cross-sectional width of the seal ring 54. Therefore, a high pressure chamber is formed at the tip of the float valve, and when the liquid pressure in the high pressure side passage increases, the float valve 55 is pushed toward the cylinder block 12 by that force, maintaining airtightness with the cylinder block. become. Furthermore, the 6th
As shown in the figure, a thrust plate 56 is provided at a position facing the float valve 55, and this plate is provided at the ninth position to maintain the rotational balance of the cylinder block 12. Equipped with 5 fixing screws
8 to the front cover 50.

With the above configuration, the airtightness of the valve can be improved very easily, so that a high-performance, high-output rotary pump can be easily provided.

Note that the above valve can be made into a self-cutting float valve by appropriately selecting the area ratio, so it is not limited to the above embodiment.

〔Effect of the invention〕

As described above, according to the present invention, a fluid machine having a simple structure and having a highly accurate valve mechanism is provided.

[BRIEF DESCRIPTION OF THE DRAWINGS] The drawings show an embodiment of the fluid machine of the present invention, and FIG. 1 is a sectional view of the main part of a near compressor, and FIG. Figure 3 is a sectional view taken along ■-m in Figure 1.
Figure 4 is a vertical sectional view of the main part of another implementation row of the same compressor,
FIG. 5 is a cross-sectional view of a main part of a hydraulic pump to which the present invention is applied, and FIG. 6 is a cross-sectional view taken along the line -■ in FIG. 3... Side plate, 5... Rotating shaft, 12... Cylinder block, 28... Seal ring, 29... High pressure chamber, 30... Float valve, 3D... High pressure side passage.

Claims (5)

[Claims] 1. A fluid machine in which a piston is disposed in a through hole of a cylinder block that is in a fixed relationship with a rotary shaft supported by the piston, and a discharge force or a rotational force is obtained by the reciprocating motion of the piston, the side plate forming a high pressure chamber and the cylinder block. A float valve is disposed between the end faces, and a seal ring is disposed around the high pressure chamber to form a high pressure chamber between the float valve and the side plate, and the float valve is pressed against the cylinder block. fluid machine. 2. A fluid machine according to claim 1, wherein the high pressure chamber is formed by a gap formed at least inside the seal ring and between the side plate and the float valve. 3. The fluid machine according to claim 1, wherein the float valve has a convex cross section and is disposed on a stepped surface formed on the inner circumference of the high pressure chamber via a seal ring. . 4. 3. A fluid machine according to claim 2, wherein the float valve is disc-shaped and is brought into contact with an end face of a cylinder block. 5. In a fluid machine in which a piston is disposed in a through hole of a cylinder block that is in a fixed relationship with a rotary shaft supported by the piston, and a discharge force or rotational force is obtained by the reciprocating motion of the piston, the end face of the cylinder block is connected to the high pressure chamber and the cylinder block. A fluid machine characterized in that the lid is closed by a float valve disposed between the end faces of the cylinder block and pressed against the end face of the cylinder block.