JPS5834247A - Disk spring pair - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to hydrostatic or pneumatic fluid pumps or motors, and to devices such as machines and vehicles in which the respective pumps or motors are used. In order to economically improve the pressure range of the device, improvements were made to the piston and piston shoe assemblies, one other improvement being the use of hydrostatic bearings and their communication with the pressurized space. It is done for. This is done for hydrostatic bearings at the ends of the rotors as well as for hydrostatic bearings in the center between the two respective rotors. Also considered is the problem that the resulting fluid, such as water, does not have good lubricating properties. Accordingly, variations of disc springs have been used to enable pumps or motors to operate with non-lubricating fluids without the use of closely fitted pistons glued within the cylinder.

It is therefore an aim of the present invention to overcome at least some of the limitations of the prior art, thereby improving the prior art devices and
and to improve new and useful pumps, motors, machine tools, or equipment or vehicles using such new pumps or motors.

BACKGROUND OF THE INVENTION a) Field of the Invention The present invention relates basically to the field of conical disc springs, in particular two disc springs forming a disc spring pair and six pairs of springs mutually reciprocating themselves. , relating to a centered disc spring.

b) Description of the Prior Art Conventional disc springs, to the best of the applicant's knowledge, currently consist of a tapered cone with a hole in the center. Two equal such springs were placed opposite each other. The two springs thereby meet either at the outer periphery of the disk or on a radially inner circle close to a central hole in the disk. When assembling a plurality of conventional springs, generally a center guide pin extends through the center hole of the disk to center the individual disk springs relative to each other.

SUMMARY OF THE INVENTION The main object and aim of the present invention is to provide a disk spring pair spring having the ability to self-center the springs of one or more disk spring pairs.

Thereby, the internal guide pins of conventional disc springs are not required and friction of the springs sliding along a common central rod can be avoided.

Another object of the invention is, in particular, to provide disc springs with a device capable of causing them to act as a pump, so that non-lubricating fluid can be discharged by the spring set of non-sliding surfaces bounding the non-lubricating fluid. It is.

Other aims, objects and details of the invention are, for example, to provide: Namely: 1) two axially opposed polygons having a conical portion, an outer portion and a central hole, and having radially inner and outer portions circularly formed around the central hole; A disc spring pair consisting of a disk, one of the springs forming a circular spring, the other of the springs forming an outward bending spring, and the circular bending spring having the center upper hole of the circular bending spring. an inner portion bent axially from said conical portion to form a substantially cylindrical portion as said inner portion in close contact with said outer bent spring, said outer portion at the outer periphery of said outer bent spring; and an outer portion which bends axially from said conical portion to form a substantially cylindrical portion.

The outward bend defines an inner surface that defines the central hole and forms an inner seat.

The circular bend forms an outer surface defining an outer circumference of the circular bend, thereby forming an outer seat.

The circular spring and the outer curved spring are arranged axially opposite each other in order to together form the disk spring pair.

The inner seat of the outer bending spring faces the inner part of the circular bending spring, or the outer seat of the circular bending spring faces the outer part of the outer spring.

2) The disc spring pair of 1), wherein when the outer seat of the circular bending spring is disposed within the outward bending spring, the outer seat faces the outer portion.

The inner seat faces the inner portion of the circular bend when the inner portion is placed in the outer bend.

3) The disk spring pair of 1), wherein the circular spring has a first substantially radially planar portion between the inner portion and the conical portion, the planar portion being at one end thereof. Prepare a seal seat.

The outer bend comprises a substantially cylindrical extension on the inner seat that substantially matches the outer diameter of the inner portion of the circular spring.

A second substantially radially planar portion is provided between the outwardly bent extension and the conical portion, thereby providing a sealing surface at one end of the second planar portion.

The circular spring has a sealing seat portion between the conical portion and the outer portion of substantially U-shaped cross section, the cross section opening substantially in a direction opposite to the direction of the inner portion. Forms a circular seal seat groove.

A third substantially radial planar portion is provided between the conical portion and the outer portion for forming a seat cover at one end of the third planar portion of the outward bend.

4) A disk spring pair according to 3), wherein said circular spring is arranged in said outer bending spring of said spring pair, and a second inner bending spring of the other spring pair of such spring pair is arranged in said outer bending spring of said spring pair. When the inner portion is placed within the extension of the outward curve spring, the sealing surface faces the sealing seat and the sealing cover faces and closes the sealing groove. .

5) In the disc spring pair of 4), a seal ring, at least partially deformable, is inserted in the sealing groove between the seal seat, the extension, and the seal surface. 6) The disk spring pair of 3), wherein the seal seat portion extends from the conical portion in the same axial direction as the axial direction of the inner portion of the inward spring.

Thereby, an innermost space is formed radially inward from the seal seat portion of the inward spring of the spring pair.

7) A disc spring pair according to 6), wherein the body filling the dead space is in the form of a substantially planar disc of an outer diameter substantially equal to the inner diameter of said sealing seat portion, and the outer diameter of said sealing seat portion is substantially equal to the inner diameter of said sealing seat portion. having a hole of a diameter substantially equal to the diameter, when the spring of the spring pair is compressed;
It is inserted between the springs of the spring pair to fill the innermost space.

8) A disc spring pair according to 6), wherein a plurality of such spring pairs are assembled axially to each other about a common axis, and with the exception of one endmost spring, the disc spring pairs of said disc spring pairs are The majority of the springs have a central passageway extending axially through the spring, and the endmost spring at one end of the disc spring pair closes the internal chamber formed by the spring pair. a central inner portion free of said passageway to form a section;

9) The disk spring pair of 8), wherein the plurality of disk spring pairs are assembled into a hollow body having an open end. the terminal spring is attached to the thrust body;
The thrust body is supported by a rotatable slide shoe.

The sliding shoe has a suitably shaped sliding surface that slides along the outer surface of an eccentric cam rotating with the rotating shaft, so that the spring pair is configured such that when the eccentric cam rotates with the shaft, It is compressed and decompressed periodically.

1o) 9V) A disc spring pair, said hollow body being closed by a portion of a cover at an axial end opposite said open end, said hollow body being suitable for said compression and decompression of said spring pair. The apparatus includes an inlet device and an outlet device having an inlet passage and an outlet passage, as well as a device for periodically opening and closing the inlet passage and the outlet passage in a timing relationship.

Thereby, the internal chamber between the springs acts as a pumping chamber when the eccentric cam rotates with the shaft or when the periodic compression and depressurization is performed by other suitable drive devices.

At that time, the slide shoe is at least partially guided into a part of the hollow body to prevent the shoe from shifting its position.

Said internal chamber is effectively utilized for the discharge of a first fluid of non-lubricating fluid, which then surrounds said hollow body, said shoe and said cam (a space is formed between said outer surface, said sliding surface, A second fluid having a high lubrication capacity is provided to at least partially lubricate a surface between the shoe and the thrust body.

At that time, the slide shoe has a pressurized space when the spring of the spring pair is compressed, and the sliding surfaces of the thrust body, the slide shoe, and the cam are periodically filled with high-pressure lubricating fluid. It is equipped with an end face and a passageway device for lubricating the

When the 10 spring pair set pump assembly is installed in a machine or vehicle having a pump or fluid motor, springs are used to connect the respective pressurized passages of such pumps or fluid motors to the aforementioned pressurized space. During the compression action, the pressurized space is communicated with the respective reno passages, openings, etc. in an appropriate and timely manner, thereby compressing the outer surface of the thrust body, slide shoe, cam, etc.
or respective control devices are provided for communicating the respective planes between the respective pluralities thereof as described above.

When a sealing device is provided between the inner surface of the hollow body and the thrust body or slide body, the sealing device is formed between the inner wall of the hollow body and the outer surface of the spring, similarly to the respective thrust body or slide shoe. The room is used as a second discharge chamber. The second discharge chambers supply a respective second fluid flow, which flow can later be combined with the fluid flow exiting the chamber between the springs, or can be sent separately from the discharge device.

It is preferable to distribute multiple spring set dispensers around a common eccentric or other suitable drive so that the flow is very even. The suction stroke of the pump is accomplished mostly by the expansion force of the disc springs of the disc spring pair.

In the case of corrosive liquids or gases, it is preferable to make the disc spring of the invention from non-corrosive materials, metals or plastics. Shows the shape part. This conical portion is common to conventional disc springs. In general, conventional disk springs consisted only of the conical portion having a central hole.

At the radially outer end of the conical portion (1) there is an outer seat (5
9) is formed, which is a roughly cylindrical outer surface. At the radially inner end of the conical part (1), an inner part (21) in the form of a hollow cylinder is formed, which slopes inwards from the inner part of the conical part (1). Stretch axially in the direction. The inner surface (28) of the inner part forms a hole (22) therein. Since the inner part (21) bends out of the conical part ('1) and bends at the radially inner end of the conical part (1), this spring is referred to here as the "internal spring". The radially outer end of the conical part (1) has the sign (
27), which ends at the outer seat (59).

In Figure 2, the conical part (2) terminates radially inwardly in an inner seat (29), which seat is roughly a cylindrical surface, in this case a cylindrical inner surface. It is. It bounds the central hole (25). At the radially outer end of the conical part (2), the spring is bent axially in an oblique direction towards the outer end of the spring, the bent part forming an outer part. Since the bent part of this spring is located in the radially outer part of the conical part, this spring is called an "outer bending spring". The outer part (23) generally forms a cylinder and has a hollow part (24) therein.

The outer bending spring of FIG. 2 and the inner spring of FIG. 1 together form a disc spring pair according to the invention.

FIG. 5 shows how the springs of FIGS. 1 and 2 are applied.

The upper spring (2) is an outward curved spring, the outer part of which surrounds the outer seat of the inner spring (1). There is a small space or clearance (26) between the outer part and the outer seat in order to allow for a slight stretch of the inner spring in the outer bending spring during compression of the inner spring (1). is equipped. The next spring pair of outwardly curved springs (2) is assembled below the upper spring pair;
Inside the inner spring of the top spring pair.

The portion is inserted into the inner seat of the outer spring of the bottom spring pair. The two pairs of springs are thereby centered with respect to each other,
Each spring of the same spring pair is automatically centered relative to the other spring of the same spring pair. Further, when adding a spring pair, the assembly is performed in the same manner.

The assembly of FIG. 5 shows that the spring pair of the present invention is self-centering and that the center guide rod is set in the center hole of the spring, as is generally required with conventional disc springs. It proves that there is no need.

A conventional and commonly used disc spring is shown in a conventional style assembly in FIG. The conventional disk springs (52, 53) shown in this figure are constructed from a simple conical section with a central hole. They are assembled axially with respect to each other, the inclinations of the cones of adjacent springs (52) (53) being in opposite directions. Spring (52) (53)
A guide pin (51) extends through the center hole of the disk spring to center the disk springs relative to each other and guide them along the guide rod (51). When the springs are compressed axially, they also contract slightly radially inward, so that conventional springs (52) (53) and guide rods (51)
) and a clearance (54) is provided between the
This was necessary. That sometimes prevents perfect line contact between conventional adjacent springs (52) (53), and sometimes the contact between two conventional adjacent springs can be as low as 1-2%. Ta. Furthermore, this hinders the effective operation of conventional disc springs, with the disadvantage that their spring thrust deviates far from the standard spring thrust.

SUMMARY OF THE INVENTION It is therefore an object of the present invention to obviate such drawbacks of the prior art and to avoid the use of the central guide rod of the conventional disc spring.

In FIG. 3, the internal spring of another embodiment of the invention has a central conical portion (3), which extends radially inwardly into a substantially radial first radial surface portion (3). 38) extends and has a sealing seat (40) therein. Its seal seat (40
) extends inwardly in the radial direction and extends downwardly (42
) and has a guide seat (41) as the outer surface.
having a central hole or passageway (39) formed therein. The inner part (42) is also shown in FIG.

The radially outer end of the conical portion (3) is provided with a sealing seat portion (33). It effectively forms a hollow ring section with a U-shaped cross-sectional area. The interior of its U-shaped cross section forms a seal seat groove (31) and is bounded by (34). The wall (33) is substantially flat in the radial direction and the wall (32)t (34) has a circular sealing groove (31).
Forms a cylindrical outer wall and inner wall of the U-shaped seal seat portion surrounding the U-shaped seal seat.

The seal seat groove (31) opens in the axial direction in a direction opposite to the direction in which the inner portion (42) extends in the axial direction. The internal space radially towards the end of the conical part (3) < 35
> + (:37 > is formed.

In FIG. 4, the conical portion (4) extends from its radially innermost end to the second radial surface portion and has a sealing surface (45) at its upper axial end. Radially inwardly of the second radial surface part with the sealing surface (45), an extension (43) forms a cylindrical part extending axially upwards in this figure, and in seven is an inner guide. A surface (44) is formed, which guide surface corresponds to the cylindrical surface (41) of the inner part (42) of the internal spring in FIG.
) has a diameter virtually equal to the outside diameter of The spring of FIG. 4 is an out-bend spring, ie the out-bend spring of the embodiment of FIGS. The inner surface (44) is a substantially cylindrical surface and the third
It can be fitted around the extension (42) shown.

Each dimensioning must be appropriate. At the radially outer end of the conical portion (4), the spring extends into a third radial surface portion (47), at the radially outer end of which the third radial surface portion (47) has a bent outer A portion (48) is provided. Radially inside thereof, it is provided with a space (50), which extends into a conical inner space (50).

A sealing cup ζ- is formed by one of the axial end surfaces of the third radiation surface portion (47) H7. The extension (43) extends radially inwardly in the axial direction of the conical portion (4), and the bent portion, the outer portion (48), extends in the opposite axial direction. The outer portion is also provided as shown in FIG.

In FIG. 6, a preferred application of the springs of FIGS. 3 and 4 is shown. It is utilized to act as the main component of the pump. The nozzle (7) forms a hollow body with a downward opening in the drawing. The top of this figure has a top cup (-) which closes the internal space (80) towards one axis.
) is provided with an inlet device consisting of a passage which is periodically opened and closed by the The seat portion (60) is the valve seat, (11) is the valve stem, (61) is the valve spring, and (62) is the valve spring (62).
It is a retaining cover.

The opening and closing of the valve arrangement (II) acts as an inlet arrangement, as in a conventional pump. In the housing, the body or cover (7) is also provided with an outlet device (12), which outlet device has an outlet valve (12) closed by a spring device (63).
) Extending from the outlet device (I2) is an outlet passageway (13) through which the fluid to be discharged into the internal space between the respective spring sets flows.

At least one spring pair of the embodiment of the invention shown in FIGS. 3 and 4 is mounted in a hollow space in the hollow body (80). It is preferred to assemble a plurality of spring pairs as shown in Figure 4. When the pairs of springs are properly assembled against each other as shown in Figure 6, there is an internal spring space (14) between the springs. This is called the internal chamber (14).For example, a seal ring that is partially deformable (at least in part), such as a lead ring, a copper ring, or a plastic seal ring (75), has a circular seal seat groove. (31) is inserted within.

An identical seal ring of suitable matching dimensions is installed on the seal seat (
40). The respective extensions (43) of the adjacent springs of FIG. 4 encircle the respective inner portions (42) of the respective springs of FIG. The respective inserted sealing rings (75) then connect the sealing seats (40) and sealing surfaces of the two adjacent springs of FIGS. (45) and the extension part (43), and the upper end of the extension part (43) contacts a part of the seal seat part (40). The filling body (64) is assembled radially outwardly around said sealing ring (75) in the seat (40). The outer diameter of the body filling the dead space preferably corresponds to the inner diameter of the seal seat portions (33) (34) in order to fill the space (35) when the spring is compressed.

In the assembly of FIG. 6, the upper seal seat grooves (31) are closed by the bottom plane of the top cover of the body. , i.e., by the end faces of the respective radial surfaces.The seal seat portions (31) to (34) of the spring of FIG. 3 are radially inward of the respective outer portions (48) of the spring of FIG. is inserted, held and guided in the space (49) of the respective spring conical part +31 (4
) are mounted oppositely to each other in adjacent springs, so that the internal chamber (14) forms a conical space (4) when the spring returns. The plurality of interior spaces (14) are communicated by respective passageways (65) which are parts of the respective springs or holes in the respective springs. In order to eliminate dead space, or to minimize dead space in the pump arrangement of FIG. It should be the diameter. The internal space (14) is sealed by a seal ring (75). If a proper sealing of the space (14) is carried out without a seal (75), i.e. by means of a spring according to FIGS.
Instead of setting the spring of FIG. 3.4 into the pump device of FIG. 6, the spring of FIGS. 1 and 2 can be inserted therein without the seal (75).

The passage (64) in the lowest spring is eliminated, and instead the spring has a closing part (66) for closing the internal space (14) in one axial direction, at the bottom end compared to the top end. It is also preferable to prepare for Also, its closure must be effected by the thrust body (8). Thrust body (8)
At one end of the spring pair set, in this figure is on its bottom closing part (66), or on the respective terminal spring of the spring set.

In Figure 6, the thrust body (8) and the slide shoe (9) attached below it are
sliding surfaces (8) having the same radius around a common center so as to pivot relative to the thrust body (8);
3) Contact each other due to (84). The top surface of the thrust body (8) rests on the bottom of the respective spring portion of the spring pair of the invention. The end remote from the thrust body has a hollow, partially cylindrical sliding surface (88) that slides along the outer surface (88) of the eccentric cam (10) assembled below.
87) is formed on the slide shoe (9). Center (8
The eccentric cam having an axis (1) having a center line (85)
1). The respective distances between centers a (85') and (86) are the outer surface (88) and the center line (85)
When the cam (10) rotates, the surface (88) in contact with the surface (87) moves up and down.
Thereby, the spring in the hollow body (7) is periodically compressed and decompressed under its own spring force.

Each time the cam (10) and shaft (11) rotate, compression and decompression occur once. Center lines (85) and (86)
The eccentricity between them is dimensioned to accommodate the compression and decompression of the springs in the space (80).

When the pressure is reduced, the fluid passes through the inlet (11) and enters the internal space (1).
4) and from there flows under pressure through the outlet (12), where the fluid is at high pressure during each compression step, up to 20,000 to 30,000 bonds per square inch.

One of the features of the apparatus described herein is that the pump apparatus has relatively few moving parts. When installing a spring, the movement of the surface part is small, less than 1 millimeter of solder. As a result, the device is capable of discharging non-lubricating fluid into the interior space (14). In the drawing, the non-lubricating fluid is
Although the term "water" is used, other non-lubricating or lubricating fluids may be used.

On the other hand, there are movable surfaces (83) (84) (87) (88) on the thrust body (8), slide shoe (9), and cam (10).
) exist for each other. When these surfaces are not lubricated, they are bonded. Therefore, the lubricating oil labeled JOILJ is added to the internal space (80) of the main body (7), and the cam (10
) into the space surrounding the slide shoe (9) and the thrust body (8) (preferably).

The keying device (74) prevents rotation of the cam (10) on the shaft (11), the sliding shoe (9) holds it in place along the inner surface (81) of the body (7) within the space (80), It is equipped with a guide part (67) for guiding.

In Figure 6, the guide part (67) of the slide shoe (9)
) is loosely attached to the inner surface of the main body (7) with a large clearance. This is an internal chamber formed between the springs (
14) is very suitable when used only for fluid discharge. However, the guide (67)
1), and also the sealing member is fitted between the shoe (9) and the inner surface (81) of the hollow body (7).
It should be understood that provision can be made between In such a case, each inlet and outlet device is spaced (80
), and the main body (the inside of the force is the second
A discharge space is formed. The second discharge space acts parallel to the discharge space formed by the internal chamber (14) of the spring of the spring pair of the invention. When the aforementioned second discharge space (80) discharges high pressure in the respective fluid, the assembly of the body (64) filling the aforementioned dead space is an excellent pump for the second discharge space (80). Important for efficiency. Due to the absence of the filling body (64), the third
Dead spaces are formed by the spring spaces (35) in the figure, and these dead spaces (35) are connected to the second discharge chamber (
8o) results in a dead volume, which reduces the efficiency of the second discharge chamber due to internal compression loss of the discharged fluid.

Pockets for hydraulic balance, which are circular grooves (69) and (71), are provided on both end faces of the shoe (9) and are communicated together by respective holes, communicating with the intermediate passageway (72). Pressure-limiting recesses (68) (70) are provided to limit the fluid-pressured surface portions (83), (84), (87), and (88) to appropriate dimensions and communicate with the respective low-pressure spaces.

The spring is very strong and the inner chamber (14) and/or chamber (8
Since the fluid pressure discharged to surface (87) is very high,
(88) and the surfaces (83) and (84) are very high, and at regular intervals of the compressed moving fluid, in particular, each highly pressurized lubricating fluid is transferred to the balancing recess (68).
(71) It is preferable to lead to (72). This includes a control fluid flow path (73) through a member such as a shoe (9).
control in a timely and appropriate manner. The shoe (9) has an axially flat end face which is adapted to slide along the control plane of the housing of the device (not shown), so that the passageway (73) passes through the control opening in said face of the housing. (
The supply of fluid supplied to 72) is appropriately controlled in a timely manner relative to the compression stroke. During a vacuum transfer, a low pressure acts within the passages and recesses (72) (73) (68) (71), and a high pressure acts therein during a compression discharge dispensing movement of the device.

When the arrangement of FIG. 6 is assembled or attached to a device, machine, or vehicle having a fluid pump or flow motor, the pressure lines in the respective pump or motor are routed through said housing (72). (73). There is no need to add a fluid pressure supply to the passageway (73), and the connections described herein do not overly reduce the power or efficiency of the respective pump or fluid motor.

FIG. 7 shows a spring pair according to another embodiment of the invention. The embodiment of this drawing is particularly suitable when the thrust capacity and strength of the springs of the spring pair are very high. Conical part of outward bending spring (5)
has for this purpose a radially very wide third radial surface part (58), which is a radially very wide third radial surface part (58) of a circular spring whose outer part (57) has a conical part (6). wide ℃
- It is widened in the radial direction so as to surround the fourth radiation surface portion (55). Said fourth portion (55) extends radially outwardly from the seal seat portions (32)-(34), thereby providing additional strength to the spring, and a conical portion (
5) with a bent portion (56) that fits within the outer portion (57) of the outer bending spring.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring initially to FIG. 9, the tapered member (1) has a tapered portion, such as a disc spring. It is flexible and has an axial spring force parallel to the axis of the hole (14). The disc-shaped member is hollow and has a radially inner end (7).

In FIG. 1, a plurality of such members (1) are guided together into at least one pair of members or discs. Since each member of the pair rotates 1800 times, member (1) is the shaft,
or opposite each other symmetrically with respect to a central radial imaginary plane perpendicular to the hole (14).

The seals (15) (16) are set to seal the discharge chamber or motor chamber or space between two members of the member pair or disc pair. The inlet and outlet devices are covered by my parent patent applications Nos. 224,769 and 282,990.
The working chamber, the discharge chamber or the motor chamber as known from No. The inlet and outlet devices are generally port and outlet valves or closable inlet and outlet ports.

According to my parent patent No. 282,990, such disk pairs operate satisfactorily in the subcritical range.

The sub-critical range is the range in which the strength of the discs overcomes the force that causes them to flex under pressure in the spring chamber so as to separate them from each other. If the spring chamber was under high pressure, it was necessary to tighten the two discs to prevent the disc parts and seals from separating from each other under high pressure in the sub-critical range. In that range, the force of the pressure in the spring chamber between the discs exceeded the strength of the retaining spring of the disc part (1).

Therefore, the present invention eliminates the need for expensive disc pair tightening by extending the critical pressure point between the subcritical and supercritical ranges to a higher critical pressure point. Thereby, the expensive fasteners are not required until the pressure point of the spring chamber is stretched higher.

In order to extend the pressure range between the sub-critical range and the super-critical range to higher pressures, the disc is provided with a reinforcement according to the invention.

In FIG. 9, the reinforced portion is section (3), which extends radially outwardly from the tapered section, i.e. the spring-acting section (11). In Figure 9, reinforcements (3) K are added. They extend axially from the outer part of reinforcement (3).

In Figure 10, the reinforcement of the disk is shown in the radial plane (
This is achieved from a conventional disc spring by grinding or machining the outer end portion of 25), the plane of which is at the same time one of the seat surfaces. FIG. 10 thereby provides a very simple and inexpensive disc for higher critical pressure points. Therefore, ordinary disc springs, which are available on the market at very low prices, can also be used.

However, note that the disc spring has reduced effective travel.

In FIG. 11, another simple reinforcing disk is shown which has a spring action to raise the pressure to a higher pressure with a critical pressure point. Here, the outer end is formed as a flat disk (33), which in this figure constitutes a reinforcement part. A radially inner portion extends radially inwardly from the tapered portion (31) and an outer portion (33) extends from the other seat surface (3
5) Form.

In Figures 9 to 11, the inclined stroke part (11 (21) (
31) of the ejectable visible disc having a stroke ('!.

As shown in these figures, step "S" can be performed. In order to extend the life of the disk of the invention, the strength appearing in that part of the member should be considered. Itinerary “S”
`` is shorter (・), and the life is extended because the strength of the material changes between values closer together than in the case of a long (・stroke ``S''. Details (I have a large influence on the life and the maximum allowable stroke per unit time.

When the members of the invention shown in FIGS. 9 to 11 are used as a pump, the top holding plate (10) and the bottom holding plate (10) or the support plate (10) are used.
0) are assembled. These top and bottom plates form end plates when the axis of the member is placed horizontally. The pump head of FIG. 9 is assembled at one end of the pump member set and the stroke drive is set at the other end of the member set. The parent patent application shows sample details of the pump head and drive for driving the stroke "S" of the member.

In Figure 29 a simple sample pump head is shown. It is placed as a pump head (28) on one end surface (seat surface) (26) or (36) or (6) of the set of FIGS. 9, 10 and 11. The head plate (28) has a large mouth valve (18) and an outlet valve (19).

The valves are supported by springs (29). In place of these valves, other inlet and outlet devices can be provided, if desired.

FIG. 9 also shows that in this case the intermediate seal, or inner seal (
It is desirable to have a ring plate (If) between the opposing parts so that a sealing seat can be obtained for the plastically deformable seal (15). The end plate (1o) is fitted with members (1) (21) (31) to form a seal seat for the end seal (16).
More generally a smaller inner diameter is obtained. These end seals (1
6) is also a plastically deformable material, such as Q-+). The central outer ring plate (11) must have a relatively large outer diameter in order to retain sufficient radial strength against radial deformation. Also, the ring plate (n) (10) is flat in the radial direction,
This plate is easily ground with a surface grinder to create parallel axial end faces.

It is important to prevent empty space, or dead volume. This is because the volume of the discharge chamber inside the spring pair of the present invention,
or because the internal volume of the member of the pair is filled with fluid.

However, the fluid is at least slightly compressible and becomes significantly compressible at the high pressures desired by the pump of the present invention.

Therefore, the dead space filling body (13) is a pump chamber,
That is, it is assembled inside the working chamber. Those filling bodies (13
), the pump will have reduced quantitative efficiency due to the compressibility of the fluid.

The dead space filler (13) reduces the amount of fluid in the discharge chamber and also reduces the amount of compression of the discharge chamber. Therefore,
The dead space filler (13) is made of an incompressible material such as steel, iron, carbon fiber, etc. A passage (14) must be provided to allow fluid in the bottom part of the pump chamber to flow to the top part of the pump chamber and vice versa.

The filler (13) usually has a central radial, directional extension IJ7g (12) which also acts as a dead space filler. At the same time, it can act as a seal holder to hold the central seal (15) in place.

The end plates (10) and the central radially extending plate (12) also have tapered spring acting portions (1) (21) (3) of the part of the invention.
Acts as a support for 1). The tapered spring-acting portions (1), (21), and (31) of this member may not provide strong support in the axial direction.
1) (31) Bends axially under very high internal pressure in the threshold chamber. The pump of the invention, when the assembly of FIGS.
Can operate at atmospheric pressure). At such high pressures, even strong spring steel will flex.

Calculation of the pump discharge amount per stroke "S" of the member of the present invention is performed as follows.

The minute radiation part of the tapered part of the member is "b
R-, and each axial portion of said portion of the member is "dY", whereby the taper portion is "
It becomes "臥".

Thereby, FIG. 30 is obtained, which develops the calculation of the ejection action as shown in FIG.

The discharge amount of the tapered portion (1) of the member of the present invention is expressed by the following equation.

Vl'/) flllcRrx] (1) The radial extension of the taper portion (1') (21) (31') is indicated in Figures 9-11 by the Greek letter "delta", which represents the taper of the member of the invention. Partial molecule il(21)
(31) is half the difference between the inner diameter "d" and the outer diameter "D".

The discharge amount in the radial direction of the inner diameter rdJ per stroke "S" of the member is as follows.

Vd = rπ5 (2) From the above equation, the total discharge amount per partial stroke “f” of stroke “S” is as follows.

vr=(”/,,) t9noe f CR3-R':
) + r7 πt, 9xf (Ro-r i ) (3) From the above equation, as shown in Figures 9 to 11, the discharge amount of the pair of members is twice the amount "Vf" calculated by equation (3). becomes.

Further details regarding the members of the present invention -8109
is shown. It is Hayama Town, Kanagawa Prefecture regarding payment of expenses and information desired for the research of the report.
Available from the Rotary Engine Research Institute at 2420 Color.

Another idea underlying the invention is as follows.

That is, for example, when a fuel such as oil or gasoline is injected into the hot air inside the cylinder of an engine, this fuel is transported by an atomized jet into the hot compressed air inside the cylinder chamber at an intermediate pressure of several hundred atmospheres. Pressurized. The fuel is thereby dispersed into high velocity globules. Most evaporated or atomized fuel globules evaporate faster; the faster the injection velocity, the higher the heat, and the smaller the fuel globules molecules. The size and injection speed of the globules are naturally determined by the shape and size of the jet when they are injected, but they are also greatly influenced by the pressure at which the fuel is injected. Injection velocity is essentially a function of injection pressure according to a basic equation.

That is, W = J 2P/9 f
41 where rWJ is the velocity and P = positive pressure “rhO
” = density.

For example, when water is injected, the injection velocity, ignoring jet losses and other losses, roughly reaches the sonic speed of water of about 1400 m/s at an injection pressure of -10,000 atmospheres.

Although shown here in my parent patent, the members of the present invention can also be used as ice pumps for very high pressures of hundreds or even thousands of atmospheres.

Furthermore, as shown in my Japanese Patent Application No. 56-181,584, it is possible to eliminate dead space in an internal combustion engine, which results in a very high final pressure of compression, where the internal combustion engine Water can be injected under high pressure to speed up the combustion of the fuel and then convert it to steam very quickly. Therefore, it is possible to obtain a "steam engine by burning excavated fuel," and this steam engine performs most of the expansion work as a steam engine, making the fuel safe.
The fuel consumption of an internal combustion engine per unit of power is
This reduces fuel consumption to a fraction.

FIG. 24 shows in longitudinal cross-section an embodiment of one basic concept of the mine-fueled steam engine of the present invention.

The piston (41) together with the cylinder head (46)
It reciprocates inside the cylinder (40). The following positioning of the piston (41) is shown. That is, the dotted line (50) indicates the outer position of the piston head, the solid line (51) indicates the operation start position of the piston head, and the dashed line (52) indicates the inner position of the piston head of the piston (41).

These different positions of the piston head of the piston (41) are important for understanding the engine of the invention.

The first position (50) is the outer position, which has its maximum volume.

As the piston (40) moves up within the cylinder toward its innermost position, it generally compresses the intake air. Therefore, in a normal four-stroke engine, the large mouth valve closes.

However, in the engine of my invention as shown in Figure 24, the mouth valve (42) is always held open as the piston (41) rises from the first position to the second position. The second position (51) is the position in which the large mouth valve (42) closes the intake port (43), and when the piston (41) further rises towards its third or innermost position (52), Compression of the intake air begins. The critical position (51) is therefore called the starting position, ie the start-of-operation position.

After the piston (41) reaches its third or innermost position, the air is compressed. Preferably, it is compressed in very small quantities to very high pressures.

For example, it may be desirable to compress to a higher pressure than would be the case with a conventional four-stroke gasoline engine.

In the third position of the piston (41) I inject the excavated fuel through the injector (47) under very high pressure and in case of very rapid combustion at high temperatures the fuel is heated in hot air. very rapidly (steams) and increases the pressure and temperature.Then, when the second position is located intermediate between the first position (50) and the second position (52), the air taken in is It is important to know that the volume is only half of the maximum amount, so that it burns at a stoichiometric value of 1 in a small amount of air, i.e. half the amount of compressed air in a normal four-stroke Ganlin engine. For G'!

It requires only half the fuel compared to a regular engine. That shows that my engine uses only a fraction of the fuel excavated by a regular four-stroke gasoline engine. The illustrated sample requires only half that amount.

This gives the impression that my engine, even at its maximum volume of cylinders (40), only provides half the power of a normal four-stroke engine. However, I don't believe that (・.

This is because, according to my invention, the compressibility is very high and the temperature at the position (52) of the piston after combustion, that is, at the position (52) slightly below it during the extension stroke, is very high; My fuel globule was quickly vaporized by the high-pressure injection. As a result, the fuel burns very quickly and heat (
, was powerful. However, the combustion and heating in my engine is very fast due to my high injection pressure.
Even at high temperatures, it was not possible to heat the wall (4o) of the cylinder (4o).

Therefore, as soon as the combustion of the fuel is completed, water is injected by the first water injector (48) under very high pressure in order to obtain very small water globules at high speed during water injection. let These water spheres again deform very quickly, ie evaporate into steam.

The faster it works, the better. The rapidity of vaporization is obtained by making my water jet very high pressure. Therefore, this invention resulted in an inexpensive high pressure water pump.

When water turns into steam at atmospheric pressure, the volume of the steam is about 1600 times the amount of water being vaporized. And for example, 10
At 0 atmospheric pressure, the steam is about 80 times stronger than the water sprayed.

Therefore, on the upward stroke of the piston (41), the amount of water that has to be injected to fill the remainder of the cylinder that is not filled with air is quite small.

The water injection under high pressure can be carried out by a single water injection device (48) or in succession with several water injection devices (48) (4
9).

The actual amount of water injected is also determined by the pressure 6 in the pressure-star diagram of Figure 25, when the gas and steam are released after the extension stroke when the outlet valve (44) opens. Discharge at the outer position (50) of the piston.

FIG. 25 shows a diagram showing the relationship between volume and pressure for the engine of FIG. 24. The first position of the piston (41) (
50) is 6 or less when it is 1 in the relationship diagram between quantity and pressure in FIG. In the piston stroke from the first position (50) to the second piston position (51), strokes 1 to 2 are performed in the diagram of FIG. 25. The large mouth valve (42) then opens and the pressure remains at atmospheric pressure 1.

The piston at position 2 in the diagram of Figure 25 (4
In the second position (51) of 1), the large mouth valve (42) is closed. The piston (41) moves from its second position to its third position (52), which corresponds to position 3 in the diagram of FIG.
As the flow progresses, compression of the intake air occurs along compression curves 2-3 of FIG. Around place f3 in Figure 25,
Injection of fuel begins, fuel evaporates quickly, and combustion quickly occurs and completes, leading to an increase in pressure and temperature along lines 3-4 in the diagram of Figure 25. This is when the piston (41) is in its third position (52). Some of it leaves lines 3-4 to line 3 before going to diesel-like combustion sites 4-7. During the remainder of the combustion time, or after completion of combustion, the piston (41) begins to move down its extension stroke. For example, it moves along curve 4-5 in the diagram of FIG. Then, somewhere between positions 4 and 7.6 in the diagram of Figure 25, a jet of water occurred and the water turned into steam. In fact, the combustion and vaporization of fuels are partially mixed temporarily. The vaporization of water takes some of the heat from the combustible fuel and air mixture or from the combusted fuel and air mixture. And finally, the gas expands further until finally, in the first position of the piston (41), the gas and steam leave the cylinder (4o) along line 44-5-0 of the diagram of FIG. and expand. Accordingly, the outlet valve (44) opens near position 6 in FIG. Finally, the remainder of the steam and gas is discharged from the cylinder between positions 6 and 1 in the diagram of FIG. This takes place on the evacuation stroke of the piston (41) or, in the case of two-stroke operation, near the position 6-1 of the piston (41).

In fact, as time is required for the vaporization of the injected water, the combustion of the gas is not completely completed, as explained above, and its extension is similar to that of the currently common gas or diesel engine. Don't follow Iwao exactly. However, the actual curves 4-L7-5-6 will be known upon further development of my engine, and they will depend on the relative amounts of water injected. The relative amount of water will be relative to the amount of the total piston stroke. Also influenced by it is the percentage of the second position (51) of the piston/(41) between the first, ie inward, and third positions during the upward stroke.

In my opinion, my engine in Figure 24 has many characteristics. For example, the amount of fuel per unit of power obtained is much smaller compared to this engine. Additionally, combustion pressures occur at higher pressures and temperatures, thereby generally increasing the thermal efficiency of the engine. Furthermore, the steam from the water cools significantly below the temperature at the midpoint of the extension stroke from 4-6 in FIG. As a result, the amount of heat transferred to the walls of the cylinder (40) is significantly smaller than the respective losses in a conventional tank. As a result, losses due to heat transfer to the cylinder walls are smaller in my engine than in a normal engine.

As a result, the efficiency of my engine will be higher than that of today's ordinary internal combustion engines. Thumn's principle was that energy was transferred to the cylinder wall by heat transfer, energy was lost in the thermodynamic cycle, and energy was exhausted to the muffler, ie, from the engine. However, in my engine, the clearance loss to the cylinder wall is much smaller. And my engine uses only a fraction of the amount of gasoline required by a current normal engine with a fixed amount of cylinders (40).

My engine also has the same problem. For example, my engine must drive a water injection system to be serviced by the power generated in the engine by the injected fuel. However, the amount of energy to drive the injector is small compared to the efficiency gains obtained. Also, cars using my engine have to support water tanks, which is less comfortable than today's regular cars without water tanks. However, the effect of saving fuel and saving at the gas station when buying that fuel is very large (
, the field has a gross effect that makes the engine very fast for me.

Naturally, thermodynamic details must be followed when using this engine. Air intake must be balanced with the amount of injected fuel.

The amount of water injected must be suitable to extract heat from the combustion gases. It must be balanced by a mixture of expanded and combusted fuel and air. These details will be worked out in more detail during the development of my engine. If time permits, the thermodynamic and mathematical relationships will be worked out during said development of my engine and filed later.

FIG. 28 shows that the vehicle already employs the very high temperatures possible with the engine of FIG. 24 or FIG. 26. When the temperature is very high, for example about 3000~40
At 00°C, ordinary cast iron or aluminum cylinder walls can no longer be used. Higher pressure, higher temperature materials are used for the walls of cylinders (40), (60), and (71) in Figures 24 and 26. Such high pressure, high temperature materials then become brittle. It requires an external reinforcement or retention device.

As a result, FIG. 28 shows that each cylinder (76)
It is shown that an outer holding frame, that is, a support frame is set around the . such outer housing (SOO)
forms an outer chamber (78) or (79) around the cylinder (76).

Pressurized fluid passes through inlets (80) (81) to outer chamber (78).
) (79). It takes place momentarily inside the cylinder (76) parallel to the pressure that appears at each time. For this purpose, a discharge device for supplying pressure as described in the present invention is provided.

Therefore, as a result of the arrangement of FIG. 28, the cylinder wall (76)
Will not destroy even brittle materials. Because the pressure from the inside and the pressure from the outside are always equal, very close to each other, or at least partially equal,
lateral destructive forces, i.e. bending forces, are prevented or reduced.

Another possibility is to direct the water into the outer chamber (78) (79) in order to warm it by the heat from the cylinder wall.The effect is that the injected water is already hot and the combustion Less thermal energy is transferred from the air/fuel mixture.

Another effect is that the water in the outer chamber (78) (79) has already vaporized near the outer surface of the wall of the inner cylinder (76).
78) or (79) and used to inject into the water jet in order to vaporize the jet water into smaller globules.

The speed at which a water sphere turns into steam and the size of a water sphere, which is determined by the injection pressure, can be calculated using my 1945-1946 mathematical process called ``evaporation of fluid globules in heated air.'' However, extensive mathematical processing would be a waste of time and cannot be found immediately. They are included in my "last will" as I was born in the places where I lived at each time.

I have explained in at least one of my aforementioned continuing patent applications that high pressures can also be obtained by an external combustion engine without dead space in the compressor, so there is no separation chamber or external combustion engine. It is also possible to operate the engine with my excavated fuel as an external combustion engine with a chamber.

FIG. 26 is a schematic longitudinal section of an external combustion engine with steam excavated fuel according to the invention, which belongs to the volume and pressure diagram of FIG. 27.

At least one compressor (60) (61) (e.g. a cylinder (60) and a piston (61) reciprocating therein) directs compressed air through an outlet valve (63) and through a passageway (64). It is sent to an external combustion engine (70). For example, as shown in my Japanese patent application, oil, gasoline,
Excavation fuels such as petroleum, diesel fuel, coal, coal powder, coal blocks are injected into the injector (65) for direct combustion in the outer combustion chamber (70) in air conveyed through the passageway (64). is injected through. When there is more than one compressor, multiple passages (
64) can be provided.

After combustion of the fuel, or near the end of combustion of the excavated fuel, water is injected into the hot gas. However, the 26th
In the case shown in the figure, it is not inserted into the cylinder, but outside the combustion chamber (7).
0) is injected into the interior. Water injection is a single injection device (65)
or by a plurality of injectors (65) (66).

The ejected small-ball water steam is indicated by reference numerals (68) and/or (69). This water vaporizes and expands, as in Figure U, but in the outer combustion chamber (70), or at least partially within it. It remains in the combustion chamber (70) and flows through the passage (72) to the larger expansion cylinder (71), in which it expands under the drive of the piston (72). Applicable for seals, such as: Compressor size and stroke;
The size and stroke of the expansion cylinder (71) with the piston (72) must be in a proper relationship, and the total amount of injected fuel and water must be accommodated. The cylinder head with valves is connected to the cylinder (
71). Preferably, the valves are those of FIG. That is, the large mouth valve (62) is a cylinder (60) and/or (70) having no dead space.
is positioned instead of the outlet valve (63) with a flat front face in order to obtain a flat front surface. Further details of that valve are set forth in my aforementioned continuation application.

FIG. 27 shows the compression stroke along curve 1-2, thereby illustrating the compression of the intake air. Line 2-3 shows the constant pressurized combustion of excavated fuel in compressed air that occurs after injecting the fuel into the outer combustion chamber (70). Line 3-4 shows the vaporization of water and the expansion of water and steam at constant pressure in the outer combustion chamber (70) after injection of water. Line 4-5 shows the expansion of the gas and steam mixture at low pressure during the extension or working stroke of the piston (72). At point 5 in FIG. 27, the mixture of gas and steam flows into the cylinder (
71) remains.

FIG. 31 shows a general improvement in the power output of a crankshaft operated engine. These engines operate very effectively in motorbikes, cars, etc. However, they are too heavy to be used on vertical takeoff airplanes. Therefore, it is desirable to obtain a large power output from such an engine at a constant weight. This can be achieved in part by using, for example, my rotary valves with large inlet and outlet cross-sectional areas, as in my Japanese Patent Application No. 56-181,584. Also, my US patent application box 80
The double turbocharger of No. 7,975 also adds to the increased output power per constant weight of the engine.

However, one limit to the output power of the engine is imposed by the centrifugal force of the connecting rod surrounding the eccentric portion of the crankshaft. When the centrifugal force generated by the connecting rod reaches high revolutions per minute, the hydraulic fluid film in the crankshaft bearing can no longer support the centrifugal force and becomes very high.

The bearings tend to bond as the revolutions per minute increase over time.

FIG. 31 overcomes the rotational limitations of such engines, allowing higher revolutions per minute and thereby higher power. I increase the revolutions per minute and power per engine by using hydrostatic pockets in the crankshaft bearings at certain locations where high centrifugal forces act.

The pressure in the pocket is selected from the pressure source and the cross-sectional areas of the pocket and surrounding seal land are suitably dimensioned to enable them to accurately support the centrifugal forces generated therein. The counterbalance on the crankshaft can be partially or completely omitted, reducing the weight of the engine and increasing the power output.

Thus, according to FIG. 31, the oil pump is driven by the crankshaft. Japanese patent application cylinder 54-164
Preferably, the variable pump of one of my patents, described in No. 1,869, is used. A pump that can change the amount of fluid discharged per revolution is preferable. Oil pump or its discharge flow ('!.

It is further employed to control the pressure level of the discharged fluid.

Controlling the discharge amount and controlling the height of the discharge pressureG family, as shown in Fig. 31, the correct pressure and oil amount in the pair 1 non-fluid pressure pocket (86) (87) of my engine's crankshaft. It is adopted to control according to the revolutions per minute of the engine crankshaft in order to supply the engine.

Oil or fluid is discharged from the pump into a passageway (85) in the engine crankshaft (83). The crankshaft (83) is fitted with a nozzle or crank casing (83).
2) Rotates with the center bearing. The crankshaft (83) has a single eccentric bearing portion (
883).

According to the invention, the hydrostatic pocket (86) with surrounding seal land is connected to the eccentric portion (883) of the crankshaft.
A central crankshaft bearing is provided at the part of the crankshaft where the centrifugal force of the engine creates a load. Branch passages (85) direct pressurized fluid from the main passage (85) into respective pockets (8). As shown in this figure, the branch passages (85) are very easily formed into the crankshaft and are oriented radially and open radially outwards, where they open into the respective pressure pocket f311. . Other branch passages (85) are also branch passages directed radially from the main passage (85), which are inclined passages (88) opening into pockets (87) in the eccentric part of the crankshaft. join together.

The latter branch channel (85) is closed radially outwards by a closing body (89). eccentric fluid pressure pocket) (87)
is set in the crankshaft at that location where the centrifugal force of the connecting rod (84) is loaded. As shown in this figure, the pockets (86) (87) are diametrically opposed to the respective crankshaft portions. (pressure pocket) (87) and the cross-sectional area of the surrounding seal land are, at each time,
It is suitably dimensioned to support the centrifugal loads caused by the connecting rod (84) in connection with the fluid pressure at each revolution per minute of the crankshaft.

Passages and pockets (85) (87) (86) (88
), the proper arrangement of passages, pockets, and seal land locations and sizes in relation to the amount and pressure of sealing fluid supplied to the Only parts can be removed. Thereby, the weight of the engine is reduced, while at the same time the revolutions per minute and the output power of the engine are increased very significantly.

12-19, 22, 23, and 34, embodiments of the dis-spring device are shown, and these embodiments are similar to 198.
It is closely related to the invention of my patent application No. 224.769 filed on January 13, 2013.

Referring first to the exploded detail view of FIG. 13, the disc spring of the present invention is designated f+1. Disc spring (
1) has a flat end surface (
It has 31+4+. The spring (1) also has an inner centering seat (25).

This spring allows fluid to be delivered in this range, which I call the sub-critical range of the disc spring (1) of the pump. This subcritical range is limited to operation below the subcritical pressure of the fluid. In this sub-critical range, the spring (1) is strong enough to withstand an optical fraction of the axial force of the fluid on the spring (1) without separating from its seat, in which the disk spring is located;
Seal together with flat surfaces (3) and/or (4).

A disadvantage of single disc springs for use in pumps, compressors or motors is that the efficiency of the device is greatly reduced. The fluid acts axially under pressure on the spring, which resists this pressure by the spring force of the spring material, such as spring steel. In order to discharge with a single disc spring, the spring must have a greater resistance than the pressure loaded part to which fluid pressure is supplied. Therefore, the fluid pressure is always in this critical range where less than half of the axial force that moves the fluid axially during the dispensing stroke is so low that it is used to dispense the fluid; At least half, or slightly more than half, of the remaining force is used to compress the spring in the subcritical range of the present invention. As a result, the efficiency of a single spring in a pump in the sub-critical range is always less than 50% linear.

My first means of overcoming this problem is to use the first spring (1)
A second spring (2) is set on the first spring (1), and the second spring is mounted diametrically opposite to the first spring (1), thereby creating a gap between the two springs (1) and (2). The purpose is to form a discharge space. The axial thrust force required for discharge is the same here. This is because compressing two springs requires the same force as compressing one spring, but twice as much fluid is dispensed.

However, the length of the compression path is doubled compared to a single spring. As a result, the force remains the same, but the path of travel is doubled, so overall the compression or thrust device gains superior efficiency. However, springs (1) and (2)
The power required for this is not significantly lower than the power ratio for the fluid discharged to one single spring (1).

If the fluid pressure decreases beyond the critical pressure between the subcritical and supercritical stages, the spring (1
) and/or (2) is applied to the spring (11(2)
1 is bent and its respective end bearing surface (3) or (4
) escapes from its seat on the pump. The discharge chamber below the respective taper of the respective disk spring (1) or (2) opens and the discharge action is prevented. The pump leaks a lot of fluid and returns to the subcritical stage.

This knowledge gained from the present invention is reconciled with the disc spring arrangement of FIG.

In FIG. 12, the disc springs (o) (12) are similarly arranged together facing each other, as indicated by the reference numeral (11 (21) in FIG. 13. (8) is placed on top. The planar ring (8) is the outer ring. Inside the outer ring is placed a seal, for example an O-ring (7). Inside the O-ring (7) is the outer An inner ring (6) of the same thickness as the ring (8) is installed.This inner ring (6) serves at the same time as a dead space filler to prevent dead space in the pump chamber (61).In case of high pressure , this dead space filler (6) is important because when it is not incorporated, the fluid compresses in the hollow space, which causes discharge and effective losses (play)
+61 serves as at least one passage for sending fluid from both halves of the pump chamber (61) to the other half. A small diameter hole is placed in the center of the inner plate (6).

If the diameter of this hole is too large, compression losses will respectively occur. However, if the hole diameter is too small, the pump will have respective losses due to fluid friction, turbulence, and swirl.

The most important part of the arrangement of FIG. 12 is the provision of the tightening device (9) of the invention. Tightening device (9)
has an inner space (18) delimited by inwardly extending ring arms (9A) (9B) surrounding the outer radial part of the disc spring (11 (21). Thereby, the spring (old 2) or ( n) (12) are axially clamped together and held together. It is important that the clamping is strong enough so that the device (9) resists its own deformation. The higher the super-critical stage of the high pressure that is activated, the stronger the tightening device (9) must be.
must be kept so strong that it does not separate from the outer ring (8) between them. Because if they separate, the seal (force falls into the clearance created by that separation).

The seal then becomes sticky and the pump can no longer operate normally.

In addition, in actual design and manufacturing, the inner annular ring groove (18
) The springs (11) (12') are filled in the radial direction so as to provide space outward in the radial direction of the outer ends of the cover springs (11) (12').
Due to the discharge and compression of 2), the spring (1) + 2 + (11,
) The outer diameter of (12,) is slightly thicker.Thus, when there is no space outward in the radial direction of the spring (11F2) (11) (129, the tightening device (9) is portion prevents the radial stretching of the spring (n) (12), thereby preventing the spring (]] ) (1
2) hinders the compression and ejection action.

The inner space (18) also has a radial extent in order to allow a radial extension of each of the outer rings (8) therein. The outer ring (8) is the ring (
8) sufficiently radially wide to withstand the fluid pressure within it to prevent destruction.

In fact, a large number of disc springs (11+2+ (11,)
(12) to center axially backwards from each other in the ultra-critical range spring (+1 (21 (11) (1
A centering device is often added to 2). This is because doing this will improve efficiency.
The figure shows a centering seat (25) into which the centering body (19) is inserted together with a centering seat (26). The centering body (19) has at its other axial end a second centering seat (27). The seat (27) is the third centering seat (29) of the second centering body (2o).
A fourth centering seat (28) at the other end of the second centering body (20) fits within the seat (25) of the disc spring (1). By utilizing the centering body, a number of disc spring pairs (1) (21) are assembled rearwardly toward each other.

FIG. 12 further shows that by providing the disk springs (11) (12) with a centering part and a seat (5i (1s) (16)), the centering body can be omitted, thereby making it possible to and the centering body become an integral part. However, in any case, the centering body (19) (20) of the respective disc spring (1) (2+ (11) (12) or the centering part ( 5
) is the discharge chamber (6) located between the disc springs of the disc spring pair.
1) to allow fluid to flow to or from the passageway (
13) It has (14).

A ring play is applied to each disc spring (1) (21') to prevent axial deformation of each disc spring (11 (2+ (11) (12)) by the very high pressure abdomen of the fluid (10). (11) (12
) is placed on the outside when viewed in the axial direction. The ring plate (10) has an internal intermediate hole (17) to contain the respective centering portion or centering body (51 (19) (20)) and the sealing device.

FIG. 34 is shown below FIG. 13. this is,
Because it is simple and requires little space, the disc spring assembly of the present invention has many bright future applications. In this embodiment of the invention, the disk spring of FIG. However, this material has such characteristics that it is glued together by an adhesive material such as, for example, Epoquine resin.

When held together by surface (3) at position (23) and jointly with surface (4) at position (24), each pair of disc springs is tightly clamped together and the second The more expensive tightening device of FIG. 12 is not required. By joining the locations (24) to the surfaces (4), multiple disc spring assemblies of multiple disc spring pairs are created. This is shown in FIG.

These assemblies now operate in ultra-critical ranges as the clamping of FIG. 12 or the gluing of FIG. 34 holds together the radially outer ends of each pair of disc springs. I can do it. The pressure in the discharge chamber or motor chamber (61) now becomes very high and exceeds the sub-critical pressure.

The force required to compress the spring (1) (21 is here:
Force to send fluid 1. Or less than the force that consumes fluid in motor action. The force required to compress the spring is negligible compared to the force on the pump or on the motor. The efficiency of the pump or motor is thereby increased very significantly and becomes higher than the linear rate of 90 inches (how important it is that the inner ring (6) prevents internal compression of the fluid and ring play). Q
It can also be seen here how important it is to prevent undesirable deformation of the spring (1) +21. However, the assembly of FIG. 34 does not require the ring plate tm. Because in this assembly, the spring (11+2
+ is because they help each other against fateful transformations.

The disk springs (11) (12) of FIG. 12 are also characterized in that their ends create friction when even a small amount of solder moves radially into the clamping device (9). Must be considered. In order to eliminate this friction and obtain superior efficiency, the apparatus of FIG. 14 is often used in practice. The tightening device (9) is attached to the screw part (33).
three rings (89) tightened together by
) to (9o). However, those links (89) to (91) are as shown in FIG.
It is divided into ring segments (A), (B), (C), etc.

Segment rings (89) to (91) in this way) (
The division into A) to (X) is the tightening ring (89) (
91) and the outer part (3) of the disc spring (11(2)).

Figures 16 and 17 show that a practical solution is added to prevent disc springs (11 (segments from 21) (89) (91) (A) (B) . . . (X) from becoming dislodged. Therefore, FIG. 17 shows the disc spring f+) or (2)
It shows an annular groove (3o) in the radially outer part of.

Figure 16 shows the plane (32) for entering the respective ring groove (3o) of the respective disc spring (1) or (2).
finger-like ring segment portions (31) extending axially from
) is shown. Such a retaining part (31) is fitted with a tightening ring (
89) Prepared for (91).

In actual use, this system was used for hardened steel disc springs, and ring glue/glue segment) (89) ~
(91) is cured. Machine finishing is done with ring groove (30
) is done precisely so as not to interfere too deeply with the strength of the cover spring (1) or (2).

In practice, the water in the discharge chamber (61) of FIG. 14 was discharged at a pressure of 10,000 to 40,000 pounds per square inch. At the same time, water was kept separate from other fluids in the apparatus of FIG.

When using the apparatus of these figures, figures 14, 16, 17 and 15, the force required to compress the spring (11 (21) is equal to the force required to expel the fluid, i.e. water, at such high pressure. This device is the ultra-critical stage of my invention, working very deeply at such high fluid pressures.As a result, the efficiency of the ultra-critical range is very small compared to the very low efficiency of the sub-critical range. Very high efficiencies are effectively and reliably obtained with this embodiment of the invention.

The 14th unit with the ability to operate in the ultra-critical range of the present invention
In the illustrated sample embodiment of the invention, the pump in the right part of the figure is driven by the fluid motor in the left part of the figure.

The motor rotor (113) has a radial cylinder (
116), in which a piston (117) reciprocates. A piston shoe (119) is interposed between the piston (11?) and the stroke guide device (121). This motor is housed in the housing part (148). The pump is placed in the housing section (130). Drive fluid is supplied to the motor and cylinder (116) through the control body (120).

The motor and pump have a common axis (97), but in particular:
When the reduction gear is assembled between the motor and the pump, there is a different shaft (97). The shaft is rotatably supported in a bearing (114) and includes an eccentric cam ring portion (55). However, this part (55) may also be a separate cam ring mounted on the respective shaft. The housing part (48) comprises a head cover (48) having an inlet passage (122) and an outlet passage (123) to the mouth valve (50) and the outlet valve (49). A spring (51) holds the valve closed when it does not open. head cover (
48), the disc spring (1) is also secured by the respective seal seat (39) and seal (40) so as to seat the seat and the disc spring (1), as shown in the enlarged view of FIG.
1) has a first seat portion for holding. The outer ring plate (8), the inner ring plate (6) and the seal (
7) is assembled as shown in Figure 12, and the ring segment is assembled as shown in Figure 12.
(89) (90) (91) The tightening device consisting of (A) to (X) is assembled as already described. This disc spring (2) is supported with its inner part on the pump piston (94). The disc spring (1) is mounted, for example, on a seal (38) in a seal seat (37), as shown in the enlarged view of FIG. This seal can be replaced with a seal ring (7) if desired. Spring (2)
has the same sealing device as the spring (1) of FIG. 22 or 23. In all cases, the bottom disc spring (2) is sealed against the piston (94).

The piston (94) is provided with a K spring space (88) for closing the large mouth valve (50). The piston (94) also has a seat or hole for a centering pin (87). Centering pin (87) extends into the outlet valve passage, thereby preventing rotation, dislodgement, or pivoting of piston (94). A spatula exit chamber, ie, an operating chamber (61) is provided. The end of the piston (94) and the end of the helad cover are connected to the working chamber (
61) should be appropriately dimensioned to prevent dead spaces.

In practice, the cam ring (55) of the pump is rotated with about 500 revolutions per minute, and the spring fl) f2) is
o Compress with less than 4 strokes to extend the life of those springs. At these revolutions per minute and in these stroke ranges, 2 million strokes are possible.
1 is compressed at a ratio comparable to the maximum stroke, the end faces of the piston (94) and the helad cover (48) match, or the dead space in the working chamber (61) is only minimal. , placed so close together that they are completely absent. At high rotational speeds and high strokes compared to the maximum stroke of the disc spring, the life of this device is greatly reduced. This is one of the reasons why I prefer fluid motors to drive pumps. This is because the fluid motor can provide the desired revolutions per minute. Eccentric motors and engines generally cannot produce such revolutions per minute without the use of reduction gears.

A piston shoe (52) is located between the eccentric force cam (55) and the piston (94). That's cam (55)
The other end surfaces of the pistons (94) rotate or pivot on the other end surfaces of the piston shoes (52). Hydraulic pressure equalization recesses and sealing rings forming hydrostatic bearings are applied to both radial ends of the piston shoes (94), resulting in low friction and wear.
The dimensions of this drawing allow very large tonnage loads. The lubricating fluid (and balancing fluid) is generally oil, which is directed through passageways (95) by fluid supply pumps through respective passageways (74) to respective hydraulic balancing pockets (74). . The thrust body and seal plate portion (115) seal the supply of pressurized lubricating and balancing fluid, such as oil, to the piston shoe (74).

FIG. 18 shows an embodiment of the invention showing the simplest and cheapest pump or motor for the sub-critical range of the invention. The stroke guide (99) has an inner guide surface (156), which is also the housing of the device. It also has external inlet passages (101) for suction or supply of fluid to a number of working chambers (61). Fluid also flows through the inlet passageway (105) and into the working chamber (61) through the inlet control port (150) of the internal control body (102). The fluid leaves the working chamber (61) through the respective outlet valves or through the outlet passage (106) of said control body (102) and the outlet control vent (106), as shown in other figures.
149) and exits the working chamber (61). An internal bore (104) of the control body (102) extends through the control body (102) and throughout the device. The simplicity of this device lies in the use of a simple subsonic disc spring device, which has a seal as shown in Figures 22 and 23, the seal being shown in this figure. Disc springs (in each part of +i f21 (37
) (38) (39) (40).

Other simplicity and therefore features of this drawing are, inter alia, that there are no sliding fitting surfaces around the pump chamber (61) and no static fit of the piston in the cylinder in this embodiment. The rotors (98) have simple outcuts (22) for guiding the respective disc spring assemblies in their walls ('107). The innermost disc spring is placed at the bottom of each outboard (22). The outermost disc spring of the disc spring set is located at the bottom seat stop of the piston (36). The piston (36) also has an inward extension (109) in which a passageway (74) is formed which connects the disc spring (109) of the assembly.
11 (21) and directs fluid to or from the working chamber (6]. The outer end of the piston (36)
O) in which a piston shoe (21) is supported and can be rotated or pivoted therein. The piston shoes are provided with respective passages (74) for drawing fluid from the inlet space (101') and for directing fluid to the balancing and lubrication pocket (112).

Since this device does not require static alignment of the piston within the cylinder, it can be manufactured with rough tolerances. With the current state of the art, only the outlet valve and the outlet valve or the respective control body need be adapted. However, other parts can also be cast into exact shapes. For example, piston (3
6), the rotor (98), and the piston shoe (21) can be cast by a lost wax method or an outer shell molding method, respectively. After that, there is no need for mechanical finishing.

When assembling the device, a small amount of wrapping and drilling of passage holes is performed. Therefore, depending on your preference, this example
Even water or dirty fluids can work.

FIG. 19 shows yet another embodiment of my subcritical range disc spring pump. It has a large mouth valve (50) and an outlet valve (
49). Furthermore, it has a piston stroke drive cam (55), on which the piston (52
) slides.

The head (48) is provided with a disk spring seat (47) and the piston (52) is provided with a second disk spring seat (53). The pump or motor chamber (61) acts as in the other figures and acts as an inner passageway (13). What is compared here with the other figures is the use in this embodiment of an outer centering body (43) and an inner centering body (41) between the respective disc springs fi+ (21).

The internally centered bodies (41) are similar to the bodies (19) of FIG. 13, except that their middle portion extends radially outwards and constitutes the ring portion (10) of FIG. is formed there. The inner centering body (41) is thereby a combination of the body (19) of FIG. 13 and the ring play (10) of FIG. 12. The outer centering body has axial extensions (43), (44) forming seats for holding the radially outer ends of the respective disc springs (11+21), which also have intermediate radially Seals (37, 38, 40) of Figures 22 or 23 may also be provided if desired.

In FIG. 20, the body (48) has a working chamber (61) within which a reciprocating piston (58) seals tightly and reciprocates therein. The piston stroke drive (55) has an eccentric outer surface (56) supporting the inner surface of the piston shoe (52) thereon, thereby
2), the second piston (59), and the first piston (58).
) and to drive and guide. The first piston (58) has one end surface placed on each end surface of the second piston (59). This is done such that the first piston is radial to the axis of the moving piston. because,
This is because the exact equiaxing of the cylinder (58) and the piston (52) cannot be guaranteed by the machining K if the diameters of the first and second pistons are different. To enable radial movement of the pistons relative to each other and radially relative to their axes, the first piston (58) has a central bore (58) axially along the central axis of the piston. 69). The bottle (70) has a center hole (69)
It has a smaller diameter and is positioned within said hole (69). The retaining bin (70) allows the pin head (64) to be positioned and supported on the respective seat of the first piston (58). Its seat is sealed to the working chamber (61) by a sealing cover (63). A seal (72) is provided on one of the pistons (58) or (52) to provide a seal between them.

The retaining bins (70) also extend into respective holes in the second piston (59). It is each fastener (71
) into the piston (59). Another seal (72) is often inserted between the second piston (59) and the holding bottle (70). In this embodiment, the first piston (58) is a discharge or motoring piston and, briefly, a fluid treatment or actuation piston, and the second piston (59) is a driving piston. It is.

each hydraulic pocket) (73) is generally mti
Similarly to between the th piston (59) and the piston shoe (52), the drive guide (55) and the piston shoe (52)
), allowing large radial loads with almost no friction during operation between them. This allows the possibility of very high pressures of fluid in the working chamber (61). The passageways (74) conduct respective lubricating and balancing fluids to the hydraulic pockets (73), often under very high pressure.

The inward stroke of the working piston (58) is caused by the driving piston (58)
59) and the piston guide (55) to form the working chamber (61).
Although the outward strokes of the aforementioned first and second pistons (58) (59) are driven within the respective drive chambers (67) bounding the ends of the drive and working pistons, Driven by fluid pressure. Drive piston (5
9) has a larger diameter than the working piston (58), the pressure in the driving chamber (67) drives the driving piston downwards in the outward stroke, when the pin (70) with its assembly device moves against the working piston (58). ) to the driving piston (59) and -
Pull together along the aisle. The passageway (68) then leads the pressurized fluid to the drive chamber (67). For example, from each other attached pump.

In particular, the device of FIG. 20 introduces a non-lubricating first fluid in the working chamber (6) to the pump (the fluid is, for example, water; the second fluid in the working chamber (67) is, for example, oil The apparatus further illustrates another embodiment of the invention, which uses a contaminated fluid collection chamber (65) in conjunction with a contaminated fluid outlet passageway (66). Seals (62), such as those that sometimes occur after long-term operation under
If the piston (58) is loose, the first fluid will leak through the clearance between the outer surface of the first piston (58) and the inner surface of the cylinder wall on which the piston (58) slides. A mixture of the first fluid and the second fluid then appears. This prevents the cleanliness of the first fluid and also the cleanliness of the second fluid. For example, it will be a mixture of oil and eternity. Such mixing can be prevented by using a contaminated fluid collection chamber (65) around the first piston/(58) and flowing the contaminated fluid through its contaminated fluid outlet chamber passageway (66).

FIG. 21 shows two further embodiments of the invention.

The first is shown in the upper part of the figure, the other in the lower part.

The working body (48) has a cylinder in which the working piston, i.e. the first piston (60), reciprocates and fills the working chamber (
61) is expanded and contracted periodically. Also, a large mouth valve (5o) and an outlet valve (49) are provided as in the other drawings. The upper body, i.e. the actuating body (48), according to this embodiment is provided with a radially inwardly open annular ring groove (83) forming a spring collection chamber (83) in which a part of the spring (84) is located. ing. The deeper the ring chamber (83), the longer the life of the spring (84). (60
) respectively extend in the radial direction with respect to the vertical axis. This helps extend the life of the spring. The spring (84) drives the first piston (60) downward in its outward stroke. To this end, according to this embodiment of the invention, the actuating piston, i.e. the first piston (6o), is connected to one end of the spring (84) and the spring bed (80) so as to support the spring (84).
Center the spring seat (6) on the piston (6o).
85), and thus the spring (84) has a piston (6
0) against the bed (86), thereby pushing the piston (6o) outwardly during the extension stroke of the working chamber (61). The bottom end of the piston (60) is flat.

Another embodiment of the invention in the bottom part of this figure shows a second piston (59) below the first piston (86). The second piston has one end with a flat end surface, the end surface of which is supported by the flat end surface of the first piston. The effect of FIG. 20 is thereby reversed. The drive piston (59) in FIG. 20 drives the drive piston (59) on the inward stroke, and the working piston 60) drives the drive piston (59) on the outward stroke. Thereby, the upper body (48) and the lower body (148)
) is saved. The piston stroke guide (55) together with its outer surface or guide surface (56) is constructed in the same manner as in FIG. The piston shoe (52) connects the drive piston (59) and the stroke drive body (55).
) and the stroke guide surface (56), and one end surface (57) of the first piston shoe is interposed between the stroke guide surface (56) and the second piston shoe along the stroke guide surface (56).
It slides as shown in Figure 0.

The bottom end of the second or drive piston (59) is formed by a second edge of radius (77) around the central part (78). Thereby, the second point (76), i.e.
The end (76) is in the shape of a ball or part of a cylinder, depending on whether the center (78) is a point or a central circle. The second end surface of the piston shoe (52)
9) has a complementary shape to the shape of the end face (76), which has the sign (75) and in fact has a radius (77) about the center (78), similar to that of the piston end face (76). It has dimensions of a second end surface of the piston shoe (52);
The center (78) has the shape of a hollow ball or part of a hollow cylinder, depending on whether it is the center point or the center line. If it is a center line (78), this center line must be perpendicular to the longitudinal axis of the drive piston (59). The drive piston (59) on its inward stroke engages the actuating piston (60).
), and its inward stroke is guided and driven by stroke guides (55) and (56) as shown in FIG.

The large radius (77) compared to the longitudinal diameter radius of the piston has a relatively large force to support large loads, thereby allowing the device to have a very large pressure in the working chamber (61). Operates under high pressure. In this drawing, the piston reciprocates in a radial direction, so the first and second ends or faces are radial end faces. The cylinder and piston axes are also radial in this drawing. However, with respect to the piston axis, these axes are longitudinal and axial axes, and if viewed from the end, with respect to the axes of the piston and piston shoe,
Stretch radially. The piston shoe (52) has a hydraulic balancing pocket (73) on its radial end face (75) (57). However, although the fluid pressure introduced therein is supplied as shown in FIG. 14 in this drawing, it may occasionally be supplied as shown in FIG. 20.

The bottom body (148) is a bottom outcup for guiding each finger or arm (81) of the piston shoe (52).
(80). In a rather primitive manner, such a device has already been proposed in my patent no. 3,874.271. According to this embodiment of the bottom portion of FIG. 21, also shown in FIG. 20, the outcut (80) extends deeper into the bottom body (148) and is located deeper than the center (78). They extend beyond the center (78) and into the bottom body (148). Piston shoe arm (81)
It also extends beyond the center (78) and deep into the outcut (80). The end of the arm (81) is connected to the outcut wall (
forming a guide end (79) which is guided along (82). A feature of this device is that the end guide (79) is essentially at the radial height of the center of the drawing, ie the pivot center (78). This allows the piston shoe to be completely retained and guided within the outcut (80);
Prevents the end guide (79) from slipping out of the outcut (80) or separating from the guide m (82).

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view of an internal spring, Fig. 2 is a longitudinal sectional view of an externally curved spring of the present invention, and Fig. 3 is another one.
4 is a partial sectional view of another embodiment of the external bending spring of the present invention; FIG. 5 is a longitudinal sectional view of a spring pair set of a plurality of spring pairs shown in FIGS. 1 and 2. FIG. 6 is a longitudinal section through a portion of the dispensing device, which is also a radial section, in which the springs of FIGS. 3 and 4 are assembled. FIG. 7 shows a portion of the pair of springs of FIGS. 3 and 4, particularly those springs with radial extensions to allow for greater thrust and greater strength. FIG. 8 is a vertical cross-sectional view of a set of conventional disc springs, and the word "conventional" is indicated. In the preferred embodiment shown in FIGS. 9-11,
FIG. 94 shows an example of a tapered portion such as a disc spring having a reinforced portion and an additional reinforced portion;
The figure shows an example in which the strengthening of the disk is achieved by mechanical finishing of the outer end portion of the radial plane, and FIG. show. FIG. 12 is a longitudinal cross-sectional view of parts of a disc spring assembly of one embodiment of the invention; FIG. 13 is a similar longitudinal cross-sectional view of a related embodiment of the invention; FIG. FIG. 15 is a cross-sectional view of a part of an apparatus showing another embodiment of the invention; FIG. 15 is a cross-sectional view of another embodiment of the invention; FIG. 17 is a longitudinal sectional view of another embodiment of the disc spring portion of the present invention; FIG. 18 is a longitudinal sectional view of yet another embodiment of the disc spring portion of the present invention; FIG. 19 is a longitudinal sectional view of one embodiment of the invention; FIG. 20 is a longitudinal sectional view of one embodiment of the invention; FIG. 21 is a longitudinal sectional view of one embodiment of the invention. FIG. 22 is a longitudinal sectional view of one embodiment of the invention, FIG. 22 is a sectional view of the disc spring portion of the invention, FIG. 23 is a sectional view of the disc spring portion of the invention, and FIG.
32 are sectional views of still other embodiments of the present invention. In addition, the figure shows (1 Conical part 2 Conical part 3 Center conical part 4 Conical part 5 Conical part 6 Inner ring 70 Ring 8 Flat ring 9 Tightening device lO cam 11 Disc spring 12 Disc spring 13 Passage 14 Passage 15 Seat 16 Seat 18 Ring groove 19 Centering body 20 Centering body 21 Inner part 22 Hole 23 Outer part 24 Hollow part 25 Center hole 27 Radial outer end of conical part 28 Inner face of inner part 29 Inside Seat part 31 Seal groove 32 Wall of seal seat part 33 Wall of seal seat part 34 Wall of seal seat part 35 Internal space 37 Internal space 38 First radiation surface part 39 Passage 40 Seal seat part 41 Guide seat part 42 Inner part 43 Extension Part 44 Inner guide surface 45 Seal surface 47 Third radial surface portion 48 Bent outer portion 49 Spring space 50 Space 51 Guide pin 52 Spring 53 Spring 54 Clearance 55 Eccentric cam 56 Eccentric outer surface 58 First piston 59 Second piston 61 Operation Chamber 62 Seal 63 Seal Cover 64 Pin Head 65 Contaminated Fluid Collection Chamber 66 Contaminated Fluid Outlet Passage No changes to the contents of Figure 1)
Fig. 2 Fig. 3 &+ Fig. 4 Fig. 5 Fig. 6 Fig. 7 Fig. 8 Fig. 9 Fig. 10 Fig. 11 Fig. 12 Fig. 7 Fig. 14 Figure OLUME

Claims (1)

[Claims] 1) When the inner oil spring is disposed within the outer bending spring, the outer seat part
facing an outer portion, the inner seat portion facing the inner portion when the inner portion of the inner oil spring is disposed within the outer curve spring. 2) the inner oil spring has a first substantially radial planar portion between the inner portion and the conical portion, the planar portion having a sealing seat at one end thereof; a substantially cylindrical extension on the inner seat that substantially matches the outer diameter of the inner portion of the inner oil spring; a second substantially radially planar portion, whereby:
It is provided with a sealing surface at one end of said second planar portion, said inner and bent tube having a sealing seat portion of substantially U-shaped cross-section between said conical portion and said outer portion, said cross-section being forming a substantially circular sealing groove opening in a direction opposite to that of the inner portion; and the outer bend forming a third substantially radial groove between the conical portion and the outer portion. 2. The disc spring pair according to claim 1, further comprising a flat portion, and a seal cover formed at one end of the third flat portion. 3) said circular spring is disposed within said outer bending spring of said spring pair; Claim 1, wherein when placed and positioned within the extension, the sealing surface faces the sealing seat and the sealing cover faces and closes the sealing groove. disc spring pair. 4) at least one tapered disc spring is assembled against each face K to seal at said face and to form a hollow working chamber between the tapered space and said face;
2. Respective inlet and outlet devices communicate with and admit fluid to the working chamber during extension of the disc spring and for discharging fluid from the working chamber during compression of the disc spring. equipment. 5) The first disc spring and the second disc spring of the pair of disc springs are attached to each other, and the radially outer end of the first disc spring is above the radially outer end of the second disc spring. 2. The apparatus of claim 1, wherein the radially inwardly extending tapered portion of the second disc spring is oriented in an opposite axial direction from the tapered portion of the first disc spring. . 6) The device of claim 4, wherein the disk spring comprises at least one flattened portion having a radial plane at one radial end of the spring. 6. The apparatus of claim 5, wherein a radially flat ring having a radially flat end face is disposed between the radially outer ends of said first and second disc rings. a radially flat surface is provided at the radially outer ends of the first and second disc springs at the axial ends and facing towards the other spring of the pair of disc springs; an outer ring having an end surface parallel to a radial plane is provided between the flat surfaces of the spring; a sealing ring is inserted radially inwardly with respect to the ring; a ring is radially inwardly relative to the sealing ring, and the inner ring is radially inwardly relative to the outer ring;
5. Apparatus according to claim 4, having a radially flat end surface, the surface of the inner ring extending axially an equal distance relative to the surface of the outer ring. 8) The device of claim 4, wherein a centering body is provided at at least one radial end portion of the spring. 9) centering bodies are provided radially towards the inner and outer ends of said pair of springs, at least one of said centering bodies radially aligning said pair of disc springs with respect to the other pair of disc springs; Consists of centering
The device of claim 35. 10) a number of said disc spring pairs are mounted axially rearward to each other to form - sets of disc spring pairs, and at least one communication passage is provided between said working chambers of said disc spring pairs; an inlet device and an outlet device communicate with an actuating chamber in the disc spring pair for compressing the spring of the disc spring pair to reduce the volume of the chamber and to pump fluid from the chamber. and a thrust device, and when the thrust device moves in the opposite direction, the disc spring expands, increasing the volume of the chamber and causing fluid to flow into the chamber. Apparatus described in section. 11) around the radially outer ends of the first and second springs of the pair of disk springs the tightening device has an encircling portion, which portion is arranged around the radial outer ends of the first and second springs of the pair; 6. The apparatus of claim 5, extending radially inwardly from the radially outer end of the disk spring along the outermost radially outer end. 12) said tightening device consists of three rings, the outer ring having a retaining ring forming part, which parts extend axially towards the respective part of the other of the two outer rings; the retaining portion is provided at the radially inner end of the ring, the springs of the pair are provided at their axially outermost and radially outer ends, and the annular ring groove is provided at the radially outer end thereof; corresponds to said retaining part; said ring is divided into ring parts; each part of the three rings is individually fastened or bolted together; and said ring part corresponds to said holding part; 12. The device of claim 11, wherein each retaining portion is inserted into the ring groove of the spring. 13) The springs of the pair are made of a bondable material with spring properties, e.g. from carbon fibre, and the radially outer ends of the springs are made of a bondable material, e.g. from epoxy resin.
and wherein the radially inner ends of adjacent springs of said spring pairs are also joined axially rearwardly to each other in said plurality of said spring pairs. The device according to item 5. 14) The device of claim 4, wherein the spring is provided with a seal bed at the radial end portion of the spring, the seal bed being provided with a plastically deformable seal. 15) The device according to claim 1, wherein the fluid motor is assembled to provide a compression drive of each of the pumps forming the discharge chamber by means of at least one disc spring. 16) First a piston is arranged for axial movement within a cylinder of the body, and has an annular groove open at one end of the body, and a spring seat and a spring bed at one end of the first piston; a spring is inserted into the groove and supported by the ped; a second piston is provided in the body axially relative to the first piston; and the second piston is restricted relative to the first body. said spring moves said piston in an outward stroke;
2. The apparatus of claim 1, wherein said second piston presses against said first piston on each inward stroke. 17) The first piston is provided in the cylinder of the main body so as to move in the axial direction, the second piston is provided in the axial direction with respect to the first piston, and the holding rod is attached to the first piston. radially flexibly mounted within a respective bore, a recess in the first piston being sealed to the cylinder, and the retaining rod extending within the second piston and retaining the piston. 2. The device of claim 1, wherein said retaining rod is tightened within said second piston to prevent it from slipping out of said second piston for integral movement. 18) A fluid royal family is provided around an adjacent end of said piston, said second piston having a larger diameter than said first piston, whereby the fluid pressure in said pressure chamber increases on its outward stroke. 18. The device of claim 17, further comprising driving said piston. 19) A contaminated fluid collection chamber with a respective contaminated fluid outlet passage is separated from a chamber within the cylinder and from the pressure chamber to prevent the contaminated fluid collection from communicating with the cylinder or the pressure chamber. Claim 1, wherein said body is provided around said first piston.
The device according to item 8. 20) A piston is provided in a cylinder of the main body, one end of the piston extends from the main body, a piston shoe storage space is provided at one end of the cylinder in the main body, and each end of the piston extends into the space. said body is provided with a recessed extension extending transversely to said piston 3° from said space into said body, and said piston shoe extends into said body at least partially; enters into said space, a pivot bed and a pivot head are provided around a pivot center in said piston on said piston shoe, and a guiding extension with a guiding portion extends at least temporarily into said recessed extension. provided at the transverse end of said piston shoe so as to extend to said guide portion substantially lateral to said pivot center positioned by being guided by respective walls of said space and said recess; An apparatus according to claim 1, comprising the steps of: