DE2360181A1 - FLUID THROUGH RADIAL PISTON MACHINE, OR RADIAL CHAMBER MACHINE WITH TWO ROTORS ROTATING AT THE SAME SPEED - Google Patents

Description

Radial piston machine or radial chamber machine through which fluid flows rotate with two rr.with the same speed = the rotors.

The invention relates to a radial piston through which fluid flows - Machine with @@@ engaging in two rotors rotating at the same speed Piston connecting rods, which are used to transmit power between the conveyor chambers or swallow = arranged chambers enlarging and reducing pistons and one of the rotors are.

They are radial chamber units through which fluid flows, such as wing cells Pumps, motors or radial pistons - pumps, motors, compressors, internal combustion engines and transmissions known that are already operationally reliable and work with good efficiency.

It is also already known to have fluid flowing through them in such To arrange radial piston units two rotors rotating at the same speed; for example ate US patent 3,273,511. Also the arrangement of piston shoes between piston and a rotor for the purpose of power transmission between the two advised. For example ajs the USA patent 3,223,046 of the inventor. The former known execution is not suitable as a fluid motor and in the latter case known execution still occur high relative movements between the piston shoes d the rotor on which they slide opens. These relative movements called "high" here are already very small in themselves, because during the absolute Rotational speed of the rotor Vu = 2 R Pi n (1), with R = radius; Pi = 3.1416 and n = speed; is the relative speed between the piston shoes and the revolving rotor on which the piston shoes in the USA patent 3,223,046 only slide Vr = 4 e n (2) with e = eccentricity between the axes of the two rotors.

The value "e" is much smaller than the value "R" and hence is the Relative speed between the named parts is much smaller than the absolute one Rotational speed of the rotor on which the piston shoes slide. In practice about 5 to 10 times smaller than the latter.

The radial piston machines according to the mentioned USA patent 3,223,046 are therefore also of high efficiency and high performance and they have become in already well proven in practice in America, Europe and Asia.

Nevertheless, the units mentioned are in their efficiency and still limited in their performance, because the efficiency and the performance can can be increased further beyond what has already been achieved. That is particular this makes it possible that fluid flowed through radial piston units for still higher pressures and that the relative speed between the power transmission connecting rod # or piston shoe and the relevant rotor further reduced, so that the relative speed @@@@@ of the known design compared to that which can be realized with this invention still appears to be too high The aim of this invention is therefore the described limits of the known radial pistons To lift aggregates and a new radial piston aggregate for fluid or To create gas operation that allows even higher degrees of efficiency and performance and, moreover, especially as a radial chamber motor that is flowed through by fluid is eeeienet.

The aim of the invention is achieved in that u between the piston immersed in one rotor and piston connecting rods in the other rotor and in de: the piston concerned and the other with the same speed as the first-mentioned rotor coupled rotor are pivotably mounted.

This increases the relative speed between the piston connecting rod and the rotor in which the relevant 3-piston connecting rod is pivotably mounted reduced to an even lower value than the relative speed between the piston shoes and the rotating rotor of the USA patent 3,223,046 is. This further reduces the relative speed between the power transmission means and rotor causes a further reduction of the friction, thus a higher pressure load capacity and thus also a further increase in efficiency and performance of the unit and of considerable proportions. The said relative speed between the connecting rod of the invention and the rotor of the invention is only Vp @@ = 2 lombda r (3) with lomba = swivel angle of the piston connecting rod and r = radius of the bearing part of the piston connecting rod in the rotating rotor part, in which the piston connecting rod is pivotably mounted is.

This speed value is only a small part of the speed value of the piston shoe of equation (2) and consequently has the execution according to the invention a smaller friction path and therefore also less friction.

In order to support the goal according to the invention, in part cylindrical bearing part of the piston connecting rod in the second rotor, the arrangement of pressure fluid pockets are provided, which via bores in the piston and in the piston connecting rod of the pressure chamber are acted upon by pressurized fluid.

This will reduce the friction between the second rotor and the one in it pivoted piston connecting rods are further reduced and at the same time one more higher pressure resistance ensured by the pressure fluid, which improves the performance of the Machine increases.

It is advantageous not to place a single print field in between Piston rods and the second rotor, but several; generally two; so that at least one pressure fluid field ax = parallel offset in front of the piston axis plane and at least one other is formed behind the piston axis plane. Corresponding Connection bores are advantageously arranged in the piston connecting rod.

For the purpose of further increasing the performance and the effectiveness of the Machine of the invention, the second rotor is provided with an annular groove into which the outer webs of the first rotor containing the working chambers (cylinders) enter can. This creates the eccentricity between the center lines of the two rotors special especially large and, if the mentioned eccentricity is large is, the piston stroke is also particularly large. This increases the amount swallowed or the amount of conveyance of the machine per revolution, which again is considerable Performance = increase results, because, as is well known, performance is one of fluids The flow through the machine is proportional to the pressure and the working volume of the machine.

The aforementioned fluid pressure fields between the piston connecting rod and second, the piston connecting rods, the rotor are then on both sides of the ring groove in the second rotor arranged.

The piston rod bearings can be found on both sides of the annular groove in the second rotor encompass the relevant piston connecting rod bearing parts by more than 180 degrees, so that the piston connecting rods cannot fall out of the second rotor. in the field of The piston connecting rods can still have a large swivel angle in the ring groove in the bearing rotor execute, because @ they are less around areas of the mentioned annular groove around the bearing rotor, than 180 degrees are encompassed.

According to a preferred embodiment of the invention the piston connecting rods must be provided with swivel angle limits .. this ensures that that the piston connecting rods cannot fall out of the pistons in question, if the pistons are not secured against falling out. That simplifies the pistons in their shape and thus the manufacture of the same, making them cheaper will.

As a result of the great eccentricity between the two rotors a particularly large angle of attack and swivel angle of the piston connecting rod Rotors circulation .. This high swivel angle or swivel range is particularly important for High pressure fluid motors are desirable because it gives a compressive force on the bearing rotor almost in the direction of rotation of the bearing rotor. This direct or almost direct Tagentia @ took hold The piston force on the second, the bearing rotor, results in an almost direct torque on the Bearing rotor without conversion via tools.

According to the invention, the torque generation is therefore particularly efficient, that is to say particularly large and particularly low-loss. In order to realize this tangential attack of the piston forces on the second rotor, which, in contrast to the first, the working rotor through which the fluid flows, can be called the bearing rotor because it swivels the pivotable piston connecting rods in itself, even at high pressure in the fluid, tangential fluid pressure fields must be used provided in the circumference of the piston and designed to be larger than in the inventor's US Pat. No. 3,225,706, from which such tangential balancing of the piston is known per se. As a result of the large maximum swivel angle of the piston connecting rods of the invention, however, the size of the known tangential balancing pressure fields in the piston circumference is no longer sufficient. With precisely measured dimensioning of the tangential pressure fluid fields in the piston in question and the pressure fluid fields between the piston connecting rods and the bearing rotor, a very high percentage of the radial force of the pressure fluid from the piston crown can be transferred directly to the bearing rotor by means of pressure fluid in the tangential direction than in the direction of rotation of the bearing rotor. The piston connecting rods are then only a small part of the power transmission means and the larger part of the control means for the direction of the force application of the pressure fluid. This means that there is an almost direct application of force by the pressure fluid in the direction of rotation of the bearing rotor. The torque is then only generated mechanically to a lesser extent, but the greater part is generated by static-dynamic pressure fluid. This is the most frictionless and thus the most efficient way to produce a torque in a machine, in particular a high torque that goes beyond electrical forces.

In most practical implementations of the invention is between the two rotors a coupling means arranged that the same speed of the two Rotors secures. In the simplest embodiment, this is part of the one The rotor is designed as an internal gear and part of the other rotor is designed as an external gear. The gear parts are braked so that they can with the practically occurring eccentricities mesh between the two rotors, causing the two to run in sync Rotors is forced and the torque forces from one to the other rotor be transmitted.

The machine of the invention can have a constant or adjustable piston stroke (displacement stroke, swallowing stroke) are formed.

In the case of the controllable version, one of the rotors is known per se and therefore not shown separately, adjustable in the eccentric direction arranged. Depending on the size of the eccentric adjustment of the rotors to one another the coupling means of the rotors then engage more or less deeply into one another.

The invention is illustrated by means of one in the attached drawing Ausfuehrungsbeispieles the invention further explained.

Figure 1 is a $ § LL Ut through Figure 2 along the section @ - @; and Figure 2 is a Cross section through FIG. 1 along the section line II-II.

The working rotor through which the fluid flows, that is to say the first rotor 1 is in Housing 21 and the cover 22 in the bearings 24 and 25 mounted and circumferentially held. To the eccentricity 19 is offset to the bearing rotor, so the second rotor 2 mounted in the bearing 23 circumferentially. The camp 23 can enthrall firmly, as shown in the figures, in Geha @ use and / or Denkel 21 and / or 22 be firmly mounted or held, or it can also be in a Verstellver @ fortress (not shown because known in principle from the patent documents mentioned) in the eccentric 19 adjustable ge @@ lten or be stored.

In @@@ nterweise si @@@@ Arbeiterster 1 the radial working chambers, for example the cylinders 5, in which the working @ @, for example the pistons @ are radially or approximately radially movable, whereby the volume of the chambers 5 during periodic rotor rotation is enlarged for the absorption of fluid and is fouled for the delivery of fluid. The supply and discharge of the fluid to and from the working chambers (cylinders) 5 can take place in an axial or radial direction through the rotor channels 26 1- in a known manner. A specific term for it is not required. An exemplary axial fluid supply and discharge ring, which is particularly suitable for high pressures, is shown in FIG. It consists of the r.c1: - 'td u? ½or R- 2 @@ uisanschluessen 3 T which are each connected via the fluid chambers 33 or 34 and through the pressure body 27 to an unrelated number of the rotor channels 26, whereby fluid can flow into or out of the chambers.

Invention ne @ zass are between the protruding into the working rotor 1 Kolber @ and the bearing rotator 2, the piston connecting rods 4 according to the invention are arranged and pivoted in the betra @ @ the piston @ and the bearing rotor @.

For this, the pistons have a known spherical part or cylinder-shaped piston connecting rod bed.

According to the invention, the second rotor, the bearing rotor, has 2 for each Piston connecting rod 4, a piston connecting rod pivot bearing bed 20.

This is shown under the figures without connecting rods to his to show the preferred embodiment more clearly. It generally consists of one axially parallel bore 20, which is interrupted by the annular groove 15 in the rotor 2 or is partially interrupted. This Pleuelschwenklaberbett is on both sides of the annular groove 15 preferably extended over more than 180 degrees, whereby the brackets 41 be designed to halster the outer pivot part of the connecting rod 4 and then encompass these outer pivot parts of the connecting rod 4 by more than 180 degrees, so that the connecting rods cannot fall out of their swivel bearing bed 20.

The outer screw bearing parts of the connecting rod 4 are introduced into the pivot bearing bed 20 from one end in the direction of the rotor axis until the center of the outer pivot bearing part of the connecting rod 4 is at the level of the annular groove 15. The middle part of the connecting rod 4 concerned can then pivot very far within the annular groove 15 in the bearing rotor 2, that is to say pivot about a large pivot angle. The outer pivot bearing parts of the Pluelz 4 are cylindrical or preferably cylindrical, with an axis that is parallel to the rotor axis, and of such a diameter that they are easily held in the swivel bearing bed 20 and can be pivoted. Since these axially parallel extensions of the outer swivel bearing part of the relevant connecting rod 4 are partially encompassed by the brackets 41 of the swivel bearing bed 20 in the bearing rotor 2, the piston connecting rods 4 can no longer fall out of them once they are inserted into their pivot bearing beds in the bearing rotor 2, but pivot flawlessly in them. The middle part of the relevant connecting rod 4 is preferably narrowed in the direction of the inner pivot bearing part located in the relevant piston 3 in order to allow a large pivoting angle of the connecting rod 4. Recesses 18 for receiving a part or a corner of the rotor web 14 or stop parts for limiting the maximum pivoting angle of the connecting rod 4 can be arranged on this central part of the connecting rod 4. so that it fits into the connecting rod bed in the piston 3 and can be pivoted to it. The swivel beds and swivel bearing parts are spherical or cylindrical part-shaped with precise bottles so that they are sealed against each other against fluid loss To prevent excessive surface pressure between the swivel bearing parts of the connecting rod 4 and the swivel bearing beds in the bearing rotor 2 and in the piston 3 are in the swivel bearing parts of the connecting rod 4 oäer between the swivel bearing parts of the connecting rod @ 4 and the Swivel bearing beds are arranged in the bearing rotor 2 and the piston 3 for the high-pressure execution of the unit according to the invention. Between the piston 3 and the inner pivot bearing part of the connecting rod 4, these pressure fluid pockets are arranged either in the piston 3 or, more simply, in the inner pivot bearing part of the connecting rod 4 and denoted by 6 in the figure.

A bore extends from the inner Druckfkuidtaschen 6 11 through the connecting rod 4 into the pressure fluid pocket or pockets 12. “The borehole or channel 11 can therefore be branched into several canal branches or holes 11 may be provided. The outer pressure fluid pocket 12 could per se be arranged radially of the inner pressure fluid pocket 6, but this would possibly .. the Limit the piston stroke, because when the connecting rod 4 swings out too much, the pressure fluid pocket is then 12 was opened .. Therefore it is useful to have the pressure fluid pocket 12 in several parts to form and each one outer pressure fluid pocket 12 on the other side of the annular groove 15 of the Bearing roters 2 in the relevant outer pivot bearing part 10 of the piston connecting rod 4 to arrange. Because there is the outer pivot bearing part 10 by more than 180 degrees encompassed by the swivel bearing bed 20 and its support 41 in the bearing rotor 2 A wide swiveling out there therefore does not lead to any opening of the pressure fluid field 12. The inner pressure fluid pocket 6 is in a known manner through the bore 7 in the piston 3 from the chamber 5 is acted upon with pressurized fluid.

The tangential pressure fluid pockets 8 and 9 are arranged in the piston 3. The inflow to them is through the pivoting movement of the connecting rod 4 and the inner Pressure fluid pocket 6 controlled.

As a result, the pressure fluid pocket is awake for half a rotor revolution 8 connected to the pressure fluid pocket 6 and during the other half of the rotor revolution the pressure fluid pocket 9 is connected to the pressure fluid field 6. The pressurized fluid bags 8 and 9 are larger according to the invention than in the known technology, since the piston connecting rods of the invention have a larger pivoting angle. In the right side of Figure 2 can be seen that the pressure fluid is backward inner Pivoting part of the connecting rod 4 through the pressure fluid field 8 directly on the cylinder wall without any mechanical friction and on the other hand the pressure field 12 in the @@@@@@@@@ relevant outer swivel bearing part lo, almost directly in the tangential direction, thus in the direction of rotation again without any mechanical friction on the swivel bearing bed 20 presses in the bearing rotor 2, thereby causing it to rotate.

To make this clear - one of the connecting rods 44 is in the right one Side of Figure 2, the outer pressure field 12 is shown.

because no mechanical friction is spoken of here, so it is This means that the pressure fluid pockets the connecting rods @ 4 almost, that is to say in the current practical execution trap to 95.6 percent about printing loads are executed, so that only about 4 percent of the pressure force from the cylinder on the piston 3 frictional effects ...

So that the bearing rotor 2 is tangential under this so in the direction of rotation directed driving force can not run away without the received is to the outside to deliver, a coupling means is between the bearing rotor 2 and the working rotor t arranged. In the figure, the coupling means is on the outer bearing rotor as an internal gear and on the inner working rotor 1 it is designed as an external gear. Both interlock in the position of the smallest eccentricity between them.

In the case of an adjustable design, said gearwheel parts 16 mesh and 17 then less intertwined if the eccentricity between them is achieved by adjusting the displacement Verk @@ becomes inert.

In order to achieve a large capacity controllability, the gear parts or coupling parts 16 and 17 then correspondingly radially deep, so with corresponding large module or corresponding to a large depth of engagement.

The exemplary embodiment of the invention shown in the figures is essentially described as a hydrostatic or pneumatic motor. Vice versa however, it can also work as a pump or compressor and, instead of the second, the bearing = rotor 2 to arrange the former, the work rotor 1 around, one can conversely, the bearing rotor 2 within a hollow working rotor 1 arrange. The coupling means 16 and 17 transmit the rotation from the one Rotor on top of the other Positions 28 and 29 show fluid lines or vice versa.

through the contact pressure and control body 27 ..

Claims (1)

Claims t 1.) Radial chambers flowed through by fluid Unit with two with the same Speed rotating rotors and fluid flow through working chambers in one the rotors, characterized in that akischea den in one of the rotors (1), the working rotor (1), engaging working parts (pistons) (3) and the other the rotors, the bearing rotor (2)) piston connecting rods (4) and arranged in the said bearing rotor (2) are pivotably mounted. 2.) Unit according to claim 1 and characterized in that between the said rotors (1) and (2) both coupling means coupling the same rotational speed (16 and 17) are arranged. 3.) Unit according to claim 1 and characterized. that the named piston connecting rods (4) are also in the working parts (pistons), (3) are pivoted. 4.) Unit according to claim l, and characterized in that on said KoZbw t ela (4) outer pivot bearing parts (lo) are arranged. 5.) unit according to claim 4 and characterized in that the Pivot bearing parts (10) extending axially parallel in both directions and partially ########### roll = shaped (with a constant radius around the Pivot bearing axis) are formed. 6 ..) Unit according to claim 1 and characterized in that the Bearing rotor (2) with partly conical or partly cylindrical swivel bearing beds (20) verse = hen is. 7.) Unit according to claim 6 and characterized in that the pivot bearing parts (10) of claim 5 in the pivot bearing beds (2n) of claim 6 are arranged 8th.) Unit according to claim 6 and characterized in that the pivot bearing beds (20) with extensions (41) to partially encompass the swivel bearing parts (10) the connecting rod (4) are provided. 9.) Unit according to claim 1 and characterized. that the bearing rotor (2) with a ring notch (15) for partially receiving the ai: i working rotor (1) formed web parts (14). and the outer pivot bearing parts (10) of the connecting rods (4) are provided with outer pressure fluid pockets (12) and the said pressure fluid pockets (6) and (12) are connected to one another by means of pressure fluid lines (119). l unit according to claim 10 and characterized in that said Pressurized fluid pockets (6) via channels (7) through the working parts (3) with the working chambers (5) are connected. 12) Unit according to claim 11 and characterized in that in the working parts (piston) (3) in the direction of rotation of the rotor (1) and, in this direction opposite pressure field pockets (8 and 9), arranged by means of the edge of the Druckflui'dtasche (6) are connected to the pressure fluid pocket (6) in the inner pivot bearing part of the connecting rod (4) and are designed to be correspondingly large for the large serving angle of the connecting rod (4). 13) Ahgregat according to claim 12 and characterized in that the called pressure fluid arrangements the pressure force of the pressure fluid in the working chamber (5) in an approximately tangential direction of rotation of the rotor on the relevant parts of the mandrel of the Swivel bearing bed (2) in the bearing rotor (2) transferred, with the connecting rod (4) partially designed as power transmission means and partly as Pluidrcuk control means are. 14) Unit according to claim 1 and characterized in that the one of the rotors (1 or 2) relative to the other in order to change the difference zpschen the 'maximum and minimum working chamber size of the working chambers (5) in the direction of the eccentricity on a larger or smaller center distance between the said rotors (1) and (2) is arranged variable or controllable. 15) Unit according to claim 2 and characterized in that the Coupling means provided with parts that can be interlocked at different depths is, 16) unit according to claim 15 and characterized in that dis coupling means (16 and 17) for different axial distances between their center lines (different Eccentricities) are usable. 17) aggregate after; nspruch lo and characterized in that the said pressure fluid pockets (12) on this side and on the other side of the annular groove (15) of the bearing rotor (2) are arranged.