JPS597033B2 - piston shoe - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a piston shoe that is installed in a machine through which liquid flows, is guided along a piston shoe guide, and is assigned to a piston. 8, characterized in that this piston shoe is assigned a recess with a protective guide wall along the rotor containing the cylinder, in which case an intermediate space is maintained between said wall and the piston shoe. The piston shoe is self-centered with respect to the piston assigned to it during the discharge stroke.

Pistons, piston shoes, and piston shoe guides in devices with liquid flow are already known, but the known examples suffer from a number of drawbacks.

For example, the manufacturing process is extremely complicated and the pressure of the liquid is limited.

This is because the connection between the piston shoe and the piston shoe guide is not large enough to withstand pressures of more than 500 atmospheres for long periods of time.

This is because a joint is usually arranged between the piston and the piston shoe, the dimensions of which are smaller than the piston cross-section, and in most cases significantly smaller, so that the support plane of the joint is smaller than the piston cross-section. This is due to the fact that this connection with the piston shoe is too small to operate effectively over a long period of time at pressures of several hundred atmospheres.

Furthermore, it is already known to provide a hydraulic region or pressure fluid region between the piston shoe and the piston head and to fill this region with hydraulic pressure in order to reduce the load on the surfaces between the piston and the piston shoe.

However, even with this measure, it is impossible to maintain a pressure of several hundred atmospheres for a long time.

The dimensions of this pressure fluid area are also the same as those of a conventional piston. This is because it is too small at the piston shoe joint.

According to the invention, the above-mentioned drawbacks are eliminated, and a piston is produced which is extremely simple to manufacture and at the same time allows a maximum pressure of several hundred atmospheres. A piston shoe connection is provided.

This is achieved in that the cross section of the connecting surface between piston and piston shoe is adapted to the entire piston diameter.

The pressure fluid pocket arranged according to the invention between the piston and the piston shoe is designed with a size approximately equal to the cross-section of the corresponding piston.

In order to achieve this, it is necessary to largely avoid all guides conventionally placed between the piston and the piston shoe and to place them away from the piston.

By doing so, it becomes possible for the first time to form the entire cross section of the piston for support between the piston and the piston shoe, and high hydraulic pressure of several hundred atmospheres is possible, effectively supporting the piston and the piston shoe. It is transmitted from the piston shoe over a long period of time.

According to the invention, therefore, a recess is arranged in the rotor containing the cylinder and the piston, in which the piston shoe engages and is guided along its wall.

This makes it possible to manufacture the piston and the piston shoe very simply, with a large piston stroke and maximum efficiency, and also to allow the piston shoe to be installed loosely on the piston without an irreleasable connection between the two.

In the case of the present invention, the piston shoe is also prevented from disengaging from its seat, and for this reason, in particular, the piston shoe is always mounted on the member containing the rotor or cylinder and piston, no matter where it is located in the device. It is in a state where it is guided within the cutout.

In the two drawings which will now be used to explain the invention with reference to the illustrated embodiments, a piston shoe according to the invention is designated by the reference numeral 1, and in FIGS. In the case of FIGS. 3 and 4, they are arranged facing outward, respectively.

The piston shoes are each equipped with a piston bed 41, which has the shape of a semi-hollow sphere and serves to receive a hemispherical piston head 49 on the piston 2.

Furthermore, since the piston shoe 1 has a notch 27 formed in a tapered shape, the hemispherical piston head 49 of the piston 2 can slide into the piston shoe seat 44 from any position.

The piston shoe 1 according to the invention is provided with an outer guide surface 21 in a manner known per se, by means of which the piston shoe slides along a piston shoe guide 22 of a piston shoe guide ring 28 or tbt. Alternatively, the piston shoe 1 is provided with a piston shoe guide surface 5 in a manner known per se, and this guide surface 5 allows the piston shoe to move toward the piston 1 driver as shown in FIGS. 1 and 2. 11 along the guide surface 6.

In a manner known per se, a pressure fluid pocket 7 is provided on the outer circumference of the piston shoe, and while the piston 2 is provided with a pressure fluid communication conduit 8, the piston shoe 1 itself also has a corresponding pressure fluid communication. A conduit 48 is provided.

Note that a pressure fluid field can be provided between the piston shoe 1 and the piston 2 in a manner known per se.

In pressure fluid pockets of this type that have been implemented in the past, the space is too small to completely balance the entire lateral surface of the piston 1 with pressure fluid.

However, according to an embodiment of the invention, the diameter of the pressure fluid pocket 7 can be made to correspond to the diameter of the piston 2.

This allows significantly higher maximum hydraulic pressures in the device, for example values of more than 500 atmospheres.

This is because only by means of the piston head-shaped design according to the invention a satisfactory pressure balance can be achieved.

The piston shoe 1 according to the invention is further provided with a piston shoe extension 46 , which allows the piston shoe to extend into the notch 2 provided in the working body or rotor 40 .
3 along the wall 45.

This guidance is extremely important. This is because if the piston shoe 1 is not held in the notch 23, it will inevitably fall away from the piston head and the machine will become unusable.

Further, according to the present invention, the piston shoe is always located inside the notch 23, no matter what position the piston is in.
When the piston shoe extension 46 is in the wall 45 of the notch 23
The notch 23 and the piston shoe extension 46 are designed such that they are guided along the piston shoe.

It is possible to arrange the piston guide extension 25 in order to extend the piston guide, and also to provide a suitable chamber enlargement in order to allow the piston 2 or the piston shoe extension 46 to penetrate deeper into the chamber or cutout 23. It is also possible to arrange an opening 24.

That is, since the extension groove 50 is provided at the end of the notch 23, together with the chamber folding part 24, the stroke of the piston 2 and the piston shoe 1 can be made a little longer.

In addition, in FIG. 5, reference numeral 51 indicates a guide surface on the outer periphery of the piston shoe extension portion 46.

The arrangement of the piston shoe 1 in the notch 23< and the assignment of the piston shoe seat 44 with the tapered notch 27 make it possible to achieve a large piston stroke in the device,
In addition, a special connection between the piston shoe 1 and the piston 2 that prevents the piston shoe 1 from separating from the piston 2 is made unnecessary.

The conventional function in which the piston shoe 1 is irreleasably connected to the piston 2 is avoided by a type of connection in which the piston shoe 1 is permanently guided in the cutout 23 of the rotor 40 to 9. It is from.

At the same time, significant advantages of the invention include that the maximum pressures already mentioned are possible, that the manufacture of the piston and piston shoe is extremely simple, and that the piston guide of the piston is separated from the guide of the piston shoe. It is mentioned that a large piston stroke is achieved.

According to the invention, the device has therefore been improved in such a way that maximum efficiency is permitted and maximum pressure is guaranteed.

In the embodiments of FIGS. 1 and 2, the front pumps 1γ, 1
8 is provided, by means of which the liquid is sucked in through the line 19 and passes through the conveying conduit 16 and the suction valve 14 into the cylinder 47 .

The pressure fluid discharged from the piston 2 then passes through the discharge valve 15 and the discharge line to be discharged from the device.

The piston is driven by a shaft 12, and a piston driving body (eccentric body) 11 is disposed on this shaft, for example, via a shaft 13, so that the eccentric body 11 is connected to the piston shoe 1.
is driven once for lifting movement, and piston shoe 1 transmits this lifting movement to piston 2.

As a result, the pressure fluid is led out from the suction valve 14, via the discharge valve 15, and from the discharge pipe.

In FIG. 1, 10 indicates a bolt. In the embodiments of FIGS. 3 and 4, the rotor 4 has a suitable cylinder 4γ.
0 is driven by the shaft 13', which is supported circumferentially in the housing part 32, 31.29.

The liquid that has passed through the pipe line 33 flows into the cylinder notch or rotor control notch of the corresponding cylinder 47 via the liquid control passage 39 provided in the crimp body '36K.

Furthermore, the liquid passes from the corresponding cylinder 47 via the rotor cutout 26 into the control channel 38 and is led out of the pump through the discharge line 34.

The flow direction of the pressure fluid can also be reversed, in which case the pressure fluid enters from the discharge line 34 via the control channel 38 and the rotor cutout 26 to the cylinder 47 and leaves the cylinder to the rotor cutout 26. It flows out from the conduit 33 via the control passage 39 .

In the embodiment shown in FIGS. 1 and 2, the pressure fluid pocket 7 as a piston shoe guide is guided along the eccentric body 11, and in the embodiment shown in FIGS. The guide surface 21 as an outer circumferential surface is guided along the guide 22 of the corresponding piston shoe guide ring 28 .

In other words, the difference between the two lies in whether the piston shoe is guided inside the piston or outside the piston. The cases shown in Figures 1 and 4 correspond to the latter, respectively.

Therefore, in FIGS. 3 and 4, the crimping body 36 is crimped onto the rotor 40 by pressure fluid, and the rotor itself is crimped onto the support 3.
The state of rotation above 0 is more clearly shown.

This provides impeccable machine operating safety notes and
The machine based on the embodiment shown in FIGS. 3 and 4 is a high-pressure, high-efficiency liquid pump. Liquid cam motor. Compressosa. It can be operated as a firing motor or similar.

3 and 4, the notch 23 and the piston shoe 1 are arranged as follows, that is, the piston shoe 1 is always connected to the piston shoe 1.
It is important that the rotor 40 is configured to remain inside the cutout 23 of the rotor 40.

If there is no pressure in this machine or device, the piston and the piston shoe will separate from each other, but as soon as pressure enters or is created in the corresponding cylinder 47, the piston 2 will move in the radial direction. is pressed onto the piston shoe 1 and self-centered, while the piston head is moved along the chamfer or tapered notch 2γ to the corresponding piston bed (head) 41 or piston head 4.
9 is rotated until it seats on the piston shoe seat 44 of the piston shoe 1 and forms a tight connection therewith.

In order to take full advantage of the ease with which the components of the invention can be manufactured, the D-notch 23 in the rotor that protects the piston shoe 1 is formed deeper than the stroke of the piston shoe 1.

Although the piston and the piston shoe according to the present invention are connected to each other via the piston shoe seat 44, they are not fixedly connected and only touch each other loosely unless pressure is applied under the piston. In addition, it is not necessary for the piston shoe 1 to fit tightly into the notch 23.

This is because the piston shoe 1 is self-centered on the piston via the piston shoe seat 44 or its chamfer due to the pressure exerted under the piston.

A tight fit is not effective as it causes friction.

It is an object of the invention to prevent such friction from occurring, since when the piston shoe is centered on the piston 2, the contact between the piston shoe and the wall of the notch 23 is This is achieved by designing the piston shoes narrowly so that a perfect intermediate space is maintained between them.

By this measure, the piston shoe guides the notch 23.
Friction between the piston shoe 1 and the piston shoe 1 is avoided, so that the efficiency of the device according to the invention and thus its output is significantly increased.

Therefore, the notch 23 is not just a piston shoe guide, but also a piston shoe protector.The safety device that keeps the piston shoe from leaving its position is as follows:
In this case, the piston shoe is given a movement capacity of several tenths of a millimeter to several millimeters.

The size of the intermediate space between the piston shoe 1 and the notch 23 is such that the piston shoe seat 44 moves from the piston head 49 as follows, that is, when the no-load stroke of the device ends and the discharge stroke begins, the piston It must not be so far apart that automatic centering of the shoe 1 can no longer take place.

The piston shoe extension 46 and the wall 45 of the notch 23 can be formed cylindrical or rectangular, but it is possible to mass produce the cylinder, the piston, and the liquid-communicating rotor 9, 40, which partially includes the piston shoe. In order to be able to simultaneously mill the notches 23 in a number of rotors together, it is advantageous for both to be square in shape.

However, it is also possible to provide the notches 23 in the rotors 9, 40 by plastic working, in which case there is no need for expensive cutting.

The piston 2 according to the invention has a large piston stroke in order to obtain a large power and high efficiency, which is characterized by a cutout 23 with a chamber expansion 24 that penetrates deeply into the rotor and a wall 45 that penetrates into the rotor. This is achieved by providing a piston shoe 1 having a It is either deeply drilled or temporarily entered.

If such measures according to the present invention are not taken,
The piston stroke will remain small, the amount of medium flowing through the device will be small, and therefore no high efficiency will be achieved.

According to the invention, the axial retention of the piston shoe 1 against falling out of its associated chamber is provided by a stationary wall.

The stationary wall therefore dimensions the end of the piston shoe 1 and the protective guide wall (for example 29.31) in such a way that the piston shoe 1 and the casing part 29.31 do not come into contact with each other and no friction occurs. It is possible to design.

In the case of a device with the highest efficiency, the piston shoe is assigned a not shown but known rotary guide, on which the guide surface 21 of the piston shoe rests.

In this case, the axial safety of the rectangular piston shoe 1 is no longer provided by a stationary housing part 29,31, but by a rotating ring or a rotating part assigned to the rotor.

In that case, since the device has a plurality of cylinder groups, it can be operated as a multi-flow machine.

If a plurality of cylinder groups are arranged axially one after the other in the rotor 9, 40, a protective guide wall which rotates with the rotor or is optionally stationary is arranged between them, advantageously this stationary casing. 29 or in the guide ring 28 from the radial inside, a ring groove is drilled into which an intermediately arranged protective guide wall can be partially penetrated, so that the large piston row 8 of the machine and the high Efficiency and therefore large output can be obtained.

The device according to the invention has already been used at pressures of 800 atmospheres, with satisfactory efficiency being achieved.

The design of the piston, piston shoe and piston shoe guide in accordance with the design of the invention thus eliminates friction between the piston shoe and the lateral guides, in particular in the expansion of the pressure fluid pocket I, 48. By adjusting the size of the cross-sectional area to reach 90% K or more of the piston lateral new area, the space between the piston 2 and the piston shoe 1 and between the piston shoe 1 and its stroke guide section 6, 11.28 is largely avoided.

If the piston shoe 1 is fixedly connected to the piston, i.e. is held in such a way that it cannot fall off the piston, this piston or piston shoe has an ideally large pressure fluid area between the piston and the piston shoe. It has a holding part that limits the space for placement.

In order to increase the efficiency of a device constructed according to the invention and used under extremely high pressures, it is possible to reduce the pressure fluid area between the piston and the piston shoe by approximately 90 mm by arranging the piston shoe which is not fixedly connected to the piston. % expansion is advantageous.

[Brief explanation of drawings]

Figure 1 shows a device according to the invention (radial piston pump)
, FIG. 2 is a cross-sectional view thereof, FIG. 3 is a vertical cross-sectional view of the radial piston motor or radial piston pump according to the present invention, FIG. 4 is a cross-sectional view thereof, and FIG.
FIG. 2 is an enlarged view showing the guided state of the piston shoe 1, piston 2, and guide ring 28 shown in the figure. 1... Piston shoe, 2... Piston, 5, 6, 21... Piston shoe guide surface,
γ...Pressure fluid pocket, 8,48...
Pressure fluid communication conduit, 9, 40... Rotor, 11.
...Eccentricity L12, 13' ...Axis, 13.
...Wedge, 14...Suction valve, 15...
...Discharge valve, 16...Conveyance conduit, 17,18...
...Front pump, 19,33...Pipeline, 22
...Piston shoe guide, 23...
Notch, 24... Chamber expansion part, 25... Piston guide extension part, 26... Rotor notch, 27
...Notch, 28 ... Piston shoe guide ring, 29, 3L32 ... Casing part, 30 ... Support body, 34 ... Discharge Pipeline, 36.37... Crimp body, 38, 39...
...Control passage, 41... Piston floor, 44...
... Piston shoe a45 ... Wall, 46.
...Piston shoe extension, 4γ...Cylinder, 49...Piston head.

Claims (1)

[Claims] 1 Cylinder 47 through which liquid flows and piston shoe 1
Piston head 4 supported by piston shoe seat 44 of
9, the cylinder 47 is installed on the rotors 9, 40 and is not only provided with a notch 23 for receiving the piston shoe 1, but also has a notch 23 for receiving the piston shoe 1.
casing parts 29, 31 and a wall 45 of the rotor 9, 40 facing the cutout 23,
The outer guide surface 21 of the piston shoe 1 is guided in the piston shoe guide 22 of the piston shoe guide ring 28, and the piston shoe 1 has an outer circumferential guide surface 51 in its extension 46 to guide the outer guide surface 21 of the piston shoe 1. Notch 23
Piston shoe, characterized in that it adjusts the positioning within and between the wall 45 facing said recess 23 and said casing part 29.31.