EP0822333A2 - Internal gear hydraulic machine - Google Patents

Abstract

A rotor (5) is non-rotatably arranged on the shaft (3) in the housing (2) and has external teeth (6). Surrounding the rotor is a rotor ring (7) with inner teeth (8), working in conjunction with the outer teeth of the rotor. The rotor and the rotor ring are fitted between lateral guide surfaces of side guide parts (12,13). Between the teeth of the rotor and the rotor ring work chambers are formed, which in opposing zones form feed-in chambers (29) and feed-out chambers (31). The chambers in rotation operation correspond with control apertures (32a,32b), forming feed-in and discharge apertures connected by conduits with an inlet and an outlet.

Description

The invention relates to a hydraulic machine according to the preamble of claim 1, 2, 3 or 4.

A present hydraulic machine is simpler Construction, with a small number of Components can be realized, and it is characterized by Immunity to interference, robustness and long service life out. It also works with optional Reversal of direction of rotation and also with motor - as well Pump operation.

A hydraulic machine of the present type is in DE 42 02 466 C2. In this known The machine is the rotor and the rotor ring between two Lateral guide discs guided by the upcoming hydraulic internal pressure against the rotor and the Rotor ring are applied. In addition, they are Side guide discs against the rotor and the by springs Prestressed rotor ring. This is a first Pressure control device formed, the Side guide washers perform a valve function. In addition, a second pressure control device with a Control opening in a channel of the housing assigned to the the hydraulic pressure present Connects the interior with the outlet of the machine. The Control opening is formed by a valve that in Flow direction towards the outlet against the restoring force the spring opens. Through this pressure control device the hydraulic pressure is also controlled.

In this way, harmful contact forces of the side guide plates are avoided and the functional characteristics of the machine are improved, e.g. B. when starting and in the low load range.
For the optional operation of this hydraulic machine in left and right rotation, there are two second mirror-image pressure control devices, of which one channel is connected to the inlet and the other channel to the outlet, the control opening being formed by check valves which follow in the housing wall open on the outside and are closed by screw plugs accessible from the outside.
In this known configuration, the feed and discharge openings are arranged offset in a circumferential direction from one another in a lateral guide part, as a result of which a large axial overall length is required.
DE 33 42 131 A1 describes an annular piston machine in which a hydrostatically acting relief valve in the form of a check valve is arranged in a channel connecting the interior of the housing and its inlet. Furthermore, the rotor and the rotor ring are guided between a valve disk and a control disk, of which check valves are provided in bores in the control disk and in an adjacent housing wall, which are connected to the inlet and return lines, the check valves in each case in the flow direction to the Open the feed chambers and close in the opposite direction.
From US 3,515,496 a hydraulic machine of the toothed ring type (FIGS. 1 to 8) can be seen as a pump in which a control element with a kidney-shaped control slot can be pivoted manually in order to control the delivery rate of the pump. In the rotor (Fig. 5) or in the rotor ring (Fig. 8), pressure relief valves (pressure relief valves) are arranged in associated radial channels, which prevent harmful overpressures if the pressure chambers are not in connection with the return channels due to the respective pivoting position of the control element (see, for example, Sp .3, lines 58 to 61).

Are on a hydraulic machine of the present type made several demands. In addition to a good function and a simple, stable and reliable A long service life is also required a simple and inexpensive manufacture. Furthermore it is beneficial if significant machine functions are not accessible from the outside to a wrong one Prevent setting by unauthorized persons.

The invention has for its object in a hydraulic machine according to the preamble of claim 1 to improve running properties and durability extend.

This object is achieved by the features of claim 1 solved.

In the embodiment according to the invention according to claim 1 the hydraulic medium is at the pressure openings of both Control discs and thus between the rotor and both Control discs under pressure, forming a medium film or cushion in between. This will not only good lubrication between these parts, but it also takes place due to the hydraulic effect a relief takes place between these parts, causing the Friction and wear can be reduced.

This embodiment according to the invention is particularly well suited for such a hydraulic machine in which one or both side guide parts are mounted so as to be axially displaceable and acted against the rotor. In both of the aforementioned cases, the hydraulic intermediate cushion is formed on both sides of the rotor, so that the valve function of the first pressure control device also takes place on both sides of the rotor and therefore two first pressure control devices can be used. With this type of machine, the pressure between the control discs and the rotor and wear are reduced, the service life is extended and the running behavior is improved. It is advantageous that the relief is provided by the working pressure and is therefore proportional to it. As a result, this configuration according to the invention is particularly suitable in combination with a second pressure control device, which also works essentially in proportion to the working pressure. In the presence of a first and / or a second pressure control device, the axial compensating forces achieved by the configuration according to claim 1 are to be included in the desired total force ratio of the forces acting on both sides of the or both axially displaceable side guide parts.
Another advantage of the configuration according to the invention is that in the event of a fault increasing the pending housing pressure, for example a back pressure or a defect in the second pressure control device, the contact pressure is lower and friction and the resulting damage can be reduced or avoided.

The invention is further based on the object Hydraulic machine according to the preamble of claim 2 To be designed so that a smaller axial design is achievable.

This object is achieved by the features of claim 2 solved.

With this configuration, the axial length of the Reduce machine, e.g. about the size of one at the known configuration existing valve disc, what for certain applications of the machine, such as in particular Drive for the tool of a gripper, e.g. an excavator or the like, is advantageous because it is low Height is reached. In comparison with the generic Design will also improve the lubrication Reduces friction and extends the lifespan because of both sides of the rotor the between it and the Side guide parts existing feed and Exhaust openings provide satisfactory lubrication on both Ensure sides of the rotor.

The invention is further based on the object hydraulic machine in the preamble of claim 3 specified type so that it automatically different operating pressures and / or pressure profiles is customizable.

This object is achieved by the features of claim 3 solved.

In this configuration, at least two are second Pressure control devices provided in parallel arrangement which for a different pressure difference between the Working pressure and the pending pressure are set and thus control the different pressure difference. Although the further or each further second Pressure control device for a higher one Pressure response area is formed or set, leads or lead to a corresponding limitation a pressure increase in the working pressure, so that even at a higher operating pressure, e.g. when installed in a other device, the working pressure is limited. It is advantageous for certain operating pressures (e.g. different manufacturers with different hydraulic systems), one of the number of number corresponding to different operating pressures to provide second pressure control devices. The number can also be different. The second pressure control devices effective in pressure areas be that overlap or follow one another. The Difference in pressure control devices can be caused by different cross-sectional sizes of the associated Pressure control openings and / or spring tension in the Design as spring valves can be achieved. With these The machine functions according to the inventive configurations with regard to their pressure curve according to the preset characteristics of the Pressure control devices. Because that from the machine torque delivered by the size of each Working pressure is dependent, apply by the invention achievable advantages for the torque it delivers corresponding. Because the respective rotational speed of the Machine from the respective functional position of the first and second pressure control device, the apply advantages achievable by the invention also for the Rotation speed.

Preferably at least part of the Pressure control devices for different Operating pressures set so that the functional range of the a pressure control device at a first operating pressure ends. The other second pressure control device is indeed set for a higher pressure range, however the effective functional area achieved by the Limited pressure limit. This makes the Machine based on your preset for different Operating pressures, e.g. different manufacturers of the associated hydraulic circuit or of the machine containing device, the max. Working pressure and that Max. Torque are automatically limited, i.e. without one Change the attitude of the second Pressure control devices.

In the context of the invention it is possible to have at least one Part of the second pressure control device or all pre-adjustable or adjustable. It is it beneficial to the highest operating pressure set second pressure control device only Presettable or adjustable, but from the outside inaccessible to arrange or train because they are a Safety device for the machine can form (pressure and Torque limitation).

Works in these configurations according to the invention the machine in terms of its pressure and torque curve according to the preset characteristics of the second pressure control devices.

The pressure and torque curve can vary depending on Continuous formation of the second pressure control devices or in stages to the desired pressure or Adjust torque characteristics. This makes it possible in certain sub-ranges of the pressure or torque range the machine special pressure and torque sizes and thus also creating torque limits. It is e.g. possible for manipulation work (stacking, unstacking) of a gripper with a relative torque to determine low value so that with wrong movements, e.g. unintentionally aimed at neighboring objects no great destructive power can be exerted. It is also possible to set the maximum torque to one limit certain value. Another advantage is to see that when using the machine at different, especially higher, operating pressures Overload protection of the machine and / or the machine driven unit is reached. Furthermore, especially in the lower torque range Improve machine response and better Achieve performance utilization.

The invention is further based on the object hydraulic machine in the preamble of claim 4 specified type so that the Speed of the machine is variable.

This object is achieved by the features of claim 4 solved.

This configuration opens up several options Machine the hydraulic pressure medium in different To supply quantities per time, which is the desired result in different rotational speeds. This leaves through differently sized entrance cross sections the inputs and / or an optional summation of the Reach entrances. It is possible depending on Construction or use case only one accordingly large or multiple outputs. Not each required inputs and / or outputs are indicated by suitable Means, e.g. Screw plugs or closure parts one to close the existing screw connection. This leaves the machine by selecting certain inlets customize those applications where different Rotational speeds and / or torques are desired.

In the embodiment according to claim 13 is the second Pressure control device in a the pressure and Component limiting the return chambers integrated in the housing. This makes it simple and inexpensive to manufacture Construction achieved. The pressure control device can preferably be fully integrated into the component and thus trained in the manufacture of the component be, with special training on the housing not needed. Another advantage is that the Pressure control device is not accessible from the outside and in addition, the housing wall is not weakened, which leads to Contributes to stability. Is e.g. when executing the Pressure control device by means of a valve the valve seat worn, then all you need is an exchange of the component, whereby the housing can continue to be used.

Another advantage is that, unlike known embodiment, the junction between the second pressure control device or its connecting channel and the outlet on the one hand in the area of the proportionately small channels existing return channel system or on associated side guide part or in front of a throttle between this channel system or this side guide part and is connected to the outlet. Preferably on associated side guide part one the outlet channels connecting circumferential groove provided, and the Connection point is arranged in the circumferential groove. As a result, there is a smaller pressure difference between the pending pressure and the pressure on the Junction, and the second pressure control device can be smaller or with lower closing spring force be designed as a valve. Furthermore takes place in functional mode in the side guide part constant change of the function Return openings take place, which is the function of the second Pressure control device favors.

Features are included in the subclaims with which further improvements with respect to the above Benefits are achieved that are too simple, small and Cost-effective and safe construction methods long lifespan that improve safety and that by selecting certain of several inputs an adaptation of the machine to certain Enable functional requirements without being otherwise Changes to the machine required.

Fig. 1 eine erfindungsgemäße hydraulische Maschine im axialen Schnitt;

Fig. 2 die Maschine im Querschnitt;

Fig. 3 und 4 jeweils die Innenansicht von zwei Seitenscheiben der Maschine;

Fig. 5 eine erfindungsgemäße hydraulische Maschine im Querschnitt in abgewandelter Ausgestaltung;

Fig. 6 eine erfindungsgemäße hydraulische Maschine im axialen Schnitt in weiter abgewandelter Ausgestaltung;

Fig. 7 eine Seitenscheibe der Maschine nach Fig. 6 in axialer Ansicht;

Fig. 8 die Seitenscheibe nach Fig. 7 im axialen Schnitt;

Fig. 9 eine erfindungsgemäße hydraulische Maschine in abgewandelter Ausgestaltung im axialen Schnitt.

The invention and further advantages which can be achieved by it are described below with reference to drawings and preferred configurations. It shows

1 shows a hydraulic machine according to the invention in axial section;

Figure 2 shows the machine in cross section.

3 and 4 each show the inside of two side windows of the machine;

5 shows a hydraulic machine according to the invention in cross section in a modified embodiment;

6 shows a hydraulic machine according to the invention in axial section in a further modified embodiment;

7 shows a side window of the machine according to FIG. 6 in an axial view;

8 shows the side window according to FIG. 7 in axial section;

Fig. 9 shows a hydraulic machine according to the invention in a modified embodiment in axial section.

The main parts of the hydraulic machine 1 are one Housing 2, a shaft 3 rotatably mounted therein, one of Annular space 4 surrounding housing 2 and surrounding shaft 3, one arranged in the area of the annular space 4 on the shaft 3 and thus rotatably connected rotor 5 with a External teeth 6, one arranged in the annular space 4 and the Rotor 5 surrounding rotor ring 7, which has an internal toothing 8 has, which with the external teeth 6 of the rotor 5th cooperates and has an external toothing 9 which with an internal toothing 11 cooperates on the housing 2, two on both sides of the rotor 5 and the rotor ring 7 arranged side windows 12, 13, which at Embodiment according to FIGS. 1 and 6 by control disks 12a, 13a are formed, and feeders to be described Discharge lines for a hydraulic medium, especially hydraulic oil.

The shaft 3 preferably penetrates this in cross section circular housing 2 on one or both sides in one Feed-through opening 14 to the outside in which it passes through at least one sealing ring is sealed. The housing 2 consists of three housing parts 2a, 2b, 2c, which are coaxial arranged one behind the other and by hint shown, arranged parallel to the central axis 17 Screws 18 are screwed together. On the axial closed end of the housing 2 is a joint approach 2d with an articulated hole 2e arranged for one around the Hinge axis 2f pivotable connection of the machine 1 a holder, in particular on the gripper of a construction machine like an excavator or the like.

On both sides of the annular space 4 are in the housing parts 2a, 2c arranged cylindrical recesses 19,21 in each of which has the associated side window 12, 13 is arranged.

Outside of the step recesses 19, 21 are in the Housing parts 2a, 2c also bearing step recesses 22, 23 arranged in which the shaft 3 by means of two suitable Bearings is stored, here two roller bearings 24, 25, in which it is two each other in the present embodiment oppositely arranged cross roller bearings that can absorb relatively high axial forces. Especially then when the side windows 12,13 by control discs 12a, 13a are formed, the side windows 12, 13 each by means of a rotation lock 20 in the housing 2 secured against rotation, here by an axially parallel pin 20a.

The rotor 5 is connected by a rotary driving connection, e.g. Keyway connection 26, rotatably with that surrounded by it Section of the shaft 3 connected. It is preferred Fit the keyway connection 26 so smooth that the Rotor 5 is axially easily displaceable on the shaft 3. Furthermore, the keyway connection 26 is e.g. by suitable Column S formed so that a passage for the hydraulic medium between the bearing step recesses 22, 23 is guaranteed.

As shown in FIG. 2 in particular, each has rounded teeth and tooth gaps formed external teeth 6 am Rotor 5 and the internal toothing 8 on the rotor ring 7 a different number of teeth, the internal toothing 8 preferably has one more tooth.

This will separate teeth and gaps between teeth the external toothing 6 and the internal toothing 8 Working chambers formed by planting associated teeth at 27 separated and essentially sealed are. There is one on each side of the page constantly changing in the operation of machine 1 Longitudinal center plane 28 pressure chambers, in Fig. 2 with clockwise rotation see e.g. 29, and on the other side of the page Return chambers, see e.g. 31. The teeth of the External teeth 6 with on the inside in the Side windows 12a, 12b arranged control openings 32a, 32b together. The hole patterns of the control openings 32a, 32b in the control disks 12a, 12b are basically the same (see 3 and 4), with respect to the plane of rotation of the rotor 5 arranged in mirror image to each other and in Circumferential direction around a usual, by the tooth dimension conditional dimension are offset from each other, whereby the function of the machine is guaranteed. At Looking towards the inside of the side windows 12, 13 (Fig.3 and 4) are the two, the respective Control openings 32a, 32b and the associated pin hole 20a containing hole patterns equal to each other. Through a Swiveling the side windows 12, 13 and one against the other Twisting one side window into the one that matches Position of the rotation locks 20, here the coaxial position of the Holes 20a, the side windows 12, 13 get the right one Installation or functional position.

In rotary operation, the control openings 32a, 32b form the medium inlet side with the pressure chambers corresponding feed or pressure openings in the a side window, e.g. 12a, and on the Medium outlet side with the return chambers corresponding discharge openings in the other Side window, e.g. 12b, for the hydraulic medium, with the teeth of the rotor 5 so by covering and release cooperate in a known manner that the well-known function of the hydraulic machine 1 is guaranteed and a rotational movement between the Shaft 3 and the housing 2 takes place. With this rotation in one circumferential direction, see e.g. B. Arrow 34 leads the rotor ring 7 brought about by the toothing eccentric movements or wobbling movements in radial Direction and circumferentially from different numbers of teeth of the internal toothing Vi and due to a different cross-sectional dimensioning of the preferably having the same number of teeth External toothing Va is guaranteed. This function one present hydraulic machine 1 is known and so far need not be described further.

The control disks 12a, 12b are preferably in the Housing parts 2a, 2c arranged.

The control openings arranged on a pitch circle 32a, 32b are axially and radially inherently extending channel sections 35,36 with a preferably arranged in the associated control disc common Channel section 37,38 connected to which in the housing 2 at least one preferably radial channel section 39, 41 connects, which can form a throttle, and the one Screw-in hole 42.43 for a connection line fitting connected is. Preferably the common one Channel section 37,38 formed by a circumferential groove. As a result, it is not only possible to use radial ones Drill channel sections 36 from the outside, but it is also possible, the associated, here by a Screw hole 42,43 formed connection, on a to be placed anywhere in the housing circumference. By the associated pressure and return channels 36 formed Media infeed and outflow thus permeates the preferably cylindrical dividing line between the associated side window 12,13 and the housing 2 radially. Each side window 12, 13 has a circumferential groove 37 or 38 in the appropriate radial plane. On both sides of it are sealing rings arranged in ring grooves, which are are preferably located in the side windows 12, 13. As the 3 and 4 show, the rotation lock 20, here the Hole 20a, not symmetrical between two Control openings 12b but one-sided in between arranged, whereby at the same position of both Twist locks 20 for the side windows 12, 13 of the offset in the circumferential direction between the control openings 12a, 12b is guaranteed.

In the operation of the machine 1, not only the pressure and Return chambers filled with the hydraulic medium, but it will fill up due to existing column S and the passage of leak oil, e.g. B. on the sealing surfaces 44, 45 between the rotor 5 and the side disks, too the housing interior 40 and the storage rooms 46, 47 with the hydraulic medium, especially hydraulic oil, what purpose lubrication of the bearings is desirable. The same fills also the ring-shaped part of the housing interior 40 Clearance 48 between the external teeth 9 and the Internal toothing 11, which is also for the sake of Lubrication of the sliding surfaces of the outer toothing Va is desired.

It is advantageous to use one of the two side windows 12, 13, here the side window 12, axially immovable and the other or both existing side windows, here the side window 13 and / or the side window 12, axially slidably to arrange and by an axial thrust to act against the rotor 5 and the rotor ring 7. For this purpose, at least one spring and / or the hydraulic pressure, e.g. the housing pressure inside Serve interior 40. With an axially directed Movability must be ensured that the Side window in the axial guide of the rotation lock 20 is displaceable, what by a corresponding Play in one of the two holes 20a in the housing 2 or in the control disk 12b for the locking pin 20b is easily accessible. Besides, they are Circumferential grooves 37, 38 wider and to be dimensioned so wide, that in every sliding position of the relevant side or Control disc 12a, 13a the desired amount of medium this Place can happen.

One or both side disks 12, 13 can be axial slidably mounted in the step recesses 19, 21 and distributed by an annular or more on the circumference arranged springs 52 against the rotor 5 and the rotor ring 7 be applied. The springs 52 can be one-sided or be arranged on both sides.

In the former case (only one side window axially slidable) can the immovable side window, here the side window 12, by means of a screw or a Pin or be axially fixed by pressing, or them can be slidably mounted in the housing 2 and on a shoulder surface 2a1 of the housing 2, here 2a, issue. It should be dimensioned so thick that the her adjacent rotor ring 7 - in the present Construction - a movement game S1 to him opposite boundary surface of the annular space 48 having. The contact with the shoulder surface 2a1 is complete the tension of the spring (s) 52 specified, regardless of whether the Pressure connection through the side window 12 (connection 42) or through the side window 13 (connection 43). The Width 48a of the annular space 4 is so large that the axial Movement play S1 is present on both sides, namely also taking into account a still to be described Valve function between the side window and on the other hand rotor and rotor ring.

In order to reduce the size, is or are Springs 52 each in a recess, in particular one Ring recess 40a, arranged in the shoulder surface 2c1.

In the latter case (springs 52 on both sides) are the Side disks 12, 13 with the rotor 5 and the rotor ring 7 also taking into account the still too descriptive valve function centered elastically.

The effective on the side window 12, 13, mechanical and hydraulic loading force F1 can be the same or a little smaller or a little bigger than the opposing force F2 that the Working pressure in the pressure chambers 29 and one in the Return chambers 31 existing pressure on the side window Generate 12,13. However, the machine 1 can also be used for one desired use case be or will be set that the force F2 is less than F1. Accordingly, the size of the outer ring surface 53 is below To take into account the thrust of the spring 52. An excess of the force F1 is intended to Sealing create a certain pressure and only as large be that no harmful friction and no increased Wear on the sealing surfaces 44, 45 occurs.

This applies if one or both side windows 13 are axial are slidably mounted. In the first case, the fixed disc as an axial abutment. In the second case are the disks 12, 13 by the existing springs 52, 52a centered.

The diameter of the side windows 12, 13 is smaller dimensioned as the measured between the teeth Inner diameter of the internal toothing 11, so that the Side windows 12, 13 not on the side surfaces of the Internal teeth 11 or on the housing part 2b, but on rest against the side surfaces of the rotor ring 7.

The or both axially displaceable side windows 12, 13 thus perform a valve function and are part of one first pressure control device 49, which on the outside of the side window or windows 12, 13 hydraulic pressure p1 controls or compensates. If the Working pressure pA exceeds a certain value, the or will they be axially floating? Side windows 12, 13 somewhat against the force of the spring 52 or springs 52 spread so that the valve 49a somewhat opens and it relieves pressure to the interior of the housing 40 taking into account the aforementioned balance of forces F1 comes to F2.

The hydraulic machine 1 is a second Pressure control device 54 with a pressure control opening 54a assigned, which are arranged in a connecting channel 55 is the interior of the housing 2 with the Connects discharge side or the return of machine 1. It is the purpose of the second pressure control device 54 that Pressure difference between the working pressure pA and the pressure p1 taking into account the Force ratio F1 / F2 essentially described over the entire working range (low load operation up to Full load) or parts of the work area (e.g. low load range, medium load range or full load) about constant control and thus a harmful Increase in pressure p1 and a harmful strong pressure on the side window or windows 12, 13 too prevent. This can be done by depressurizing the Pressure p1 through the control opening 54a to the return can reach and through a pressure control opening 54a in Form a constant or adjustable choke or a control valve 54b with one against a spring force opening closing body can be reached. By a Reduction or enlargement of the throttle or Pressure control opening 54a or the spring force can be Set pressure p1 and the counterforce F1, also very good in low load range. With increasing size of the Control opening 54a and / or increasing decrease in Spring force will reduce the F1 counterforce Valve gap between the side window 12, 13 on the one hand and the rotor 5 and the rotor ring 7, on the other hand, enlarged, the effective working pressure is reduced and thus that too generated torque or the power of the machine 1 decreased.

The cross section of the pressure control opening 54a is corresponding dimensioned and the spring force adjusted or adjustable. There is a valve 54b that is already at one relatively low pressure p1 opens as special proven advantageous. The adjustability can e.g. by a threaded plug with a tool - Rotary handle element as an abutment for the valve spring can be achieved.

The first and second pressure control devices 49, 54 are with regard to their influence on the pressure p1 Effects coordinated so that an approximately constant pressure difference pA / p1 and the target Force ratio F1 / F2 is reached.

In the case of a hydraulic machine 1 which has a variable Work in the direction of rotation or in motor and pump operation are one or two, depending on the construction To provide pressure control devices 54, of which in the latter case the one with the respective inlet and the another is connected to the respective outlet. Here Valves 54b in the form of check valves are recommended 54c, which block the respective inlet connection and the open the respective outlet connection.

1, for legal and Left-handed rotation is two Pressure control devices 54 in the form of check valves 54c provided. The latter are each in one Connection channel 55 arranged in the housing extends, and each with the associated circumferential groove 37,38 connects the housing interior 40. 1 are the Connection channels 55 each through a first in the Radial plane of the associated circumferential groove 37, 38 from the outside in the housing parts 2a, 2c drilled bore 54e, a second, to the associated end face of the associated Side window 12, 13 radially from the outside into the housing part 2a, 2c drilled and into the housing interior 40, here in an annular groove 40a in the housing part 2c or in the associated Side window 12 opening bore 54f and one of the Drilled inside of the housing parts 2a, 2c, the Bores 54e and 54f intersecting bore 54g formed outside by a plug 54h are closed.

The holes 54f each have one through Cross-sectional taper formed valve seat against the a valve body, in particular a cone or a ball, is biased by a valve spring.

One or both of the second pressure control devices 54 can be preset or e.g. with a member Screw plug 54h with an outer Tool attack element - by changing the force the valve spring can be adjustable.

Because by the first and the second Pressure control device 49.54 the effective working pressure pA is determined by default or Setting the respective second pressure control device 54 a desired approximately constant output torque Set machine 1 as a function of a certain one Operating pressure that the supplied hydraulic medium having.

Preferably, the or the outlets (at Right / left rotation of the respective inlet and outlet) Machine 1, here the throttled channel sections 39, 41, Bypasses, here bypass check valves 61 in the form of Check valves assigned so that the closing body associated bypass 62 blocks in the input direction and in the exit direction opens. This is in each Functional operation of the machine 1 a forced relaxation or outflow of the hydraulic medium to the outlet guaranteed.

The bypass check valve (s) 61 may e.g. from the outside accessible in the existing chokes 39.41 bypassing e.g. ending in the circumferential grooves 37.38 and the Screw-in holes 42, 43 intersecting channel sections or be arranged oblique holes, each one Valve seat, a valve body and, a valve spring that Form the aforementioned check valve.

In an exemplary application in which a Supply line of a hydraulic supply e.g. on the connection 42 is connected, the hydraulic passes Medium first into the pressure chambers 29 where there is rotation of the rotor 5 and then to the return chambers 31, from where it goes through line sections 35 to 41 to the outlet 43 flows. In the other case, the reverse is the case. Of the Outlet is axially offset with respect to the inlet, these connections each in the radial area of the associated side window 12, 13 can be arranged.

In FIG. 1, a further second pressure control device 54.A is provided in a parallel arrangement in a bypass channel 54d parallel to the first pressure control device 54 or opening 54a, which is designed differently and is designed with a differently sized control opening 54a and / or valve spring tension or can be preset or adjustable. The further second pressure control device 54.A is set up for a higher pressure response range. It is suitable for controlling a reduction in the pressure rise in the working pressure even in higher pressure and flow ranges. The further second pressure control device 54.A is preferably set up in such a way that it limits a pressure rise above a certain value at a certain operating pressure and thus also limits the torque of the machine 1. It is also possible and advantageous to dimension the second pressure control device 54.A such that when the machine 1 is subjected to a higher operating pressure, a certain working pressure and certain torque are not exceeded. Such a machine 1 can therefore be used without readjustment for certain different operating pressures or devices, without the risk of overloading.
The further or respectively further second pressure control device 54, 54.A can have a smaller control opening 54a and / or a larger spring tension depending on the coordination of the control opening size / spring force.

Within the scope of the invention it is possible to use several, e.g. three or four or more correspondingly different ones second pressure control devices 54 arranged in parallel for a higher pressure response range or higher To provide operating pressures.

As can be seen from the drawing, it is over fluidic reasons advantageous, the one or further pressure control devices 54, 54.1 from an annular groove 40b go out on the outer peripheral edge of the side window 12 let that in the area of the shoulder surface 2a1 by a or more channels or grooves (not shown) with the Housing interior 40 is connected.

It is also advantageous to use the machine 1 with two or multiple inlets and one or more outlets for form the hydraulic medium, at least two the inlets of different sizes, e.g. through the Have channel sections 39,41 formed throttles. This makes it possible to use the machine for different purposes Set speeds. If two or more inputs with chokes of the same size or different sizes provided, it is also possible to use a targeted connection of one or more inputs to one Feed line Z or more feed lines one to get the desired rotation speed. If the optional activation of several rotation speeds is desired, this can be done by at least one Changeover valve U in the supply line Z or in the Supply lines can be achieved, e.g. manually or is electrically switchable (electromagnetic valve) (Fig. 5). The inputs and outputs that are not required are closed by suitable locking parts, e.g. B. Lock fittings or plugs.

1 and 5 are several Inlets and outlets offset in the circumferential direction arranged.

The arrangement of several different second Pressure control devices is also in combination with different input chokes 39.41 with regard to a torque limitation advantageous.

6 to 8 or 9, in which same or comparable parts with the same reference numerals are also different in several Regarding the above-described embodiments.

On the one hand, both side windows 12, 13 are also Control discs 12a, 13a formed, but both have Control discs both feed and pressure openings as also discharge openings on the respective associated Channel sections 35,36, which are interconnected are, preferably in an associated circumferential groove 37.38 open. The circumferential grooves of each side window are axially spaced apart and on both sides by sealed ring seals described above. This Control disks 12a, 13a are identical to one another and arranged in mirror image to each other, so that only one Art manufactured, stored and assembled in the housing 2 are needed. The hole patterns, i.e. on the one hand the Pressure openings and on the other hand the return openings, are axially opposite each other. The anti-rotation locks 20 are each symmetrical to the neighboring pressure or Return openings arranged so that the Control disks 12a, 13a optionally in one or the other Housing position are mountable and fit.

The choke-forming channel sections 39, 41 are each in accordance with the transverse plane of the associated one Circumferential groove 37.38 axially offset. Preferably starting from the associated circumferential groove 37 or 38 also bypasses 61 or bypass check valves to everyone Outlet and preferably also each inlet Assigned (reversal of direction of rotation), e.g. in the design according to Fig. 5. A respective bypass 61 is in particular at an arrangement of the second pressure control device 54 in the side window 12,13 advantageous because in such If there are restricted return flow conditions.

As already in the embodiment of FIG. 1 can here, too, one or both side disks 12, 13 axially displaceable and by at least one spring 52 against the Be biased rotor 5. One of the two can 6, the side window 12a, in the associated recess 19, 21 sit firmly, e.g. pressed in or it can be by the spring force of others Side window 13a against a particularly fixed axial Stop (housing) must be biased. However, it can also one centered by springs 52 on both sides Arrangement may be provided. On the related Descriptions in the embodiment of FIG. 1 is Referred.

With this configuration, one or more can Inlets and / or outlets each approximately in the level of one or both control disks 12a, 13a in the circumferential direction be staggered. If there are several Inputs can refer to at least two or all of them their preferably formed by a choke Cross-sectional size designed differently or be set. You can use one or more One and / or several different outlets second pressure control devices 54, 54.1 as described above be assigned.

Of two or more axially and circumferentially move, e.g. two or three circumferentially staggered connections A1 to A3 and A4 to A6 in the Transverse plane of each side window 12a, 13a according to FIG. 6 can one or more except for one or more outlets Inlets. Of their throttle cross sections, here the Cross sections of the channel sections 39, 41 can at least two or all be different. They don't connected connections are closed, e.g. through a stopper.

There is also an advantage of several input options in that in the event of an input defect, e.g. Damage to the Screw thread, another input same or to Not even unequal throttle cross-section can be used can.

In the embodiment according to FIG. 6, the one or the other or both side windows 12, 13 assigned inlets and outlets form a passage, whereby by reversing flow direction right / left can be realized. It is essential that at least one this port is inlet and at least one other Outlet is, that is, the inlet leads to pressure openings or an associated circumferential groove 38 and the outlet starts from return openings or one connected with it Circumferential groove 37 from.

A particular advantage of arranging two Side windows 12a, 13a each with pressure and Return openings, each connected to each other stand (channel sections 35,36 and associated circumferential groove 37a, 38), on the one hand, is that the lubrication between the rotor 5 and the side disks 12a, 13a is improved because that at all pressure openings hydraulic medium is present under pressure. On the other hand thereby hydraulic in Fig. 9 indicated by arrows Compensating forces generated, the side windows 12a, 13a too seek spread and thereby at least partially or completely compensate for those caused by the pressure Cause compressive force (surface pressure) with which the Side windows 12a, 13a by the outside of them Pressure against the rotor 5 are pressed. This Design is suitable because of the improved Lubrication for such side windows 12a, 13a, which in Housing 2 are axially immovable or because partial or full pressure equalization also for Side windows 12a, 13a, one or both of which is axial slidably supported and by at least one spring 52 is acted upon.

The side windows 12, 13 do not have to go through complete Control discs 12a, 13a can be formed. The respective Side window assigned to the inlet only needs pressure openings and the associated channels 35,36 while the other side window have pressure and return openings got to. Accordingly, the one assigned to the outlet needs Side window only to have return openings while the other must also have both openings. In these two cases, only one direction of rotation is possible, what is specified in many cases for a pump.

Furthermore, one or more second each Pressure control devices 54 in another embodiment and Arrangement, e.g. in housing 2 and / or in one or both side windows 12a, 13a.

6 to 9 is at least the Section of the pressure control opening 54a Connection channel 55, preferably the connection channel 55 overall, in the control disc 12a, 12b, the Connecting channel 55 into the associated circumferential groove 37, 38 flows. It is a stepped bore with different Bore sections 56a, 56b preferably in about axially parallel arrangement provided, against which the Step of the closing body 57 forming the pressure control opening 54a is acted upon by a spring 58, which on one of the Plug section on the inside, in particular screw plug 59, supports. From the bigger one Bore section 56b extends radially Channel section 60 to the associated circumferential groove 37, 38. The one or two existing second pressure control devices 54 are preferably the inlet and outlet sides of each other diametrically opposite in the side windows 12a, 13a arranged. If the screw hole 42a and / or 42b the Is the printing side, then the left one is Pressure control device 54 in operation and vice versa. These second pressure control devices can also be used 54 designed the same and / or different and / or be set.

6, there are several, namely four different from each other Pressure control devices provided that different Functions. Those in the same transverse plane or arranged opposite each other Pressure control devices are in each other essentially the same and have only a mirror image Function for right / left rotation.

The first pressure control device 54.1 is in one Control disc, here e.g. in the control disk 13a, arranged and at a very low response pressure set, the valve opening and the spring force of the Valve springs are relatively small. It is the purpose of the Pressure control device 54.1, the basic function pressure control due to low medium outflow guarantee. This pressure control device 54.1 is in essentially across the entire functional range of the Machine 1 opened.

Which are independent of the connections A1, A2, A4 and A5 working pressure control devices 54.2,54.3 trained for different high response pressures or set or preset, e.g. a second and a third second pressure control device 54.2,54.3, in their mode of action for different heights Print areas are set up. It can be different operating pressures of different devices and / or manufacturer act. This allows in the already described a working pressure and Torque limitation despite different operating pressures achieve, and it will be both functional and strength reasons the safety of the machine improved.

The one in a side window, here the other side window 12a, arranged pressure control device 54.4 is for a Function also or only in an even higher pressure range set, which is a maximum pressure or can also be an operating pressure. This Pressure control device 54.4 can be another Control the step range of the second pressure control device or a pressure relief valve with proportionally form a large throttle. Another is automatic Level range or a level specified for limitation an impermissible increase in pressure or to adjust the Machine 1 to another different one Operating pressure when setting a certain preferably the same torque. This Pressure control device 54.4 is preferably not adjustable or inaccessible, here inside of the housing, thereby forming a safety device is.

The function of the machine 1 according to Figure 6 is as follows explained on the basis of the connection arrangement according to FIG. 9, in which for example, the connection A1 to a pressure line and the Connection A2 are connected to a return line. The Connections A3, A4, A5 and A6 are by suitable Locking parts V such as Screw plug closed. The Pressure medium present at port A1 reaches the Print page according to the arrows to all existing ones second pressure control devices 54.1 to 54.4, whereby these are closed. They stay on the return side correspondingly set up pressure control devices 54.1. To 54.3 or, if necessary, also 54.4 in Function, being connected in parallel, for different effective response ranges Pressure control devices work. Another parallel connection of another 1 can be provided be.

Otherwise, you can choose from this configuration Connections A1 to A6 are provided for the flow passage be, causing different speeds of rotation and / or torques due to different Input chokes can be reached.

It is also possible through special Closure elements Va, which are dimensioned so long that they the connecting hole 54i in the area of the respective Block connection, optionally second Turn off pressure control devices 54. This too are adaptations to different torques and Rotation speeds in a simple and fast way reachable. If in the presence of an appropriate Operating pressure with only the second pressure control device the highest response range, see e.g. 54.4, in operation is left, a correspondingly high performance over the entire speed range can be achieved. The latter leaves e.g. at connections A3 and A6 when the reach second pressure control devices 54.2 and 54.3.

With changing direction of flow passage results each clockwise / anti-clockwise.

Claims (26)

Hydraulic machine (1) of the toothed ring type, in particular hydraulic motor, consisting of a housing (2), a shaft (3) rotatably mounted in the interior of the housing (2), which penetrates the wall of the housing (2) in a hole in a sealed manner with at least one shaft end, a rotor (5) arranged in the housing (2) in a rotationally fixed manner on the shaft (3) and having external teeth (6), a rotor ring (7) surrounding the rotor (5) with an internal toothing (8) which interacts with the external toothing (6) of the rotor (5), the rotor (5) and the rotor ring (7) being guided between lateral guide surfaces of lateral guide parts (12, 13),
- Working chambers are formed between the teeth (6, 8) of the rotor (5) and the rotor ring (7), which form supply chambers (29) and discharge chambers (31) in opposite zones, which correspond to control openings (32a, 32b) in rotary operation, form the supply and discharge openings, which are each connected to an inlet and an outlet by supply and discharge lines, and wherein one or both side guide parts (12, 13) are each formed by a control disk (12a, 13a) having control openings (32a, 32b), characterized,
that in one side guide part (12, 13) feed and discharge openings and in the other side guide part (12, 13) only feed openings or also feed and discharge openings are arranged. Hydraulic machine (1) of the toothed ring type, in particular hydraulic motor, consisting of a housing (2), a shaft (3) rotatably mounted in the interior of the housing (2), which penetrates the wall of the housing (2) in a hole in a sealed manner with at least one shaft end, a rotor (5) arranged in the housing (2) in a rotationally fixed manner on the shaft (3) and having external teeth (6), a rotor ring (7) surrounding the rotor (5) with an internal toothing (8) which interacts with the external toothing (6) of the rotor (5), the rotor (5) and the rotor ring (7) being guided between lateral guide surfaces of lateral guide parts (12, 13), working chambers are formed between the toothings (6, 8) of the rotor (5) and the rotor ring (7) and form supply chambers and discharge chambers in opposite zones, which correspond to feed and discharge openings of feed and discharge lines in rotary operation, which are connected to an inlet and to an outlet, the side guide parts (12, 13) are each mounted in a recess (19, 21) in the housing (2), wherein one or both side guide parts (12, 13) are mounted axially displaceably in the interior of the housing (2) and acted upon by the hydraulic pressure (p1) and by a spring force against the rotor (5) and the rotor ring (7) and form a first pressure control device (49), A second pressure control device (54) with at least one control opening (54a) is provided in a connecting channel (55) for setting an approximately constant pressure difference between the working pressure (pA) and the pressure (p1.) applied to the axially displaceable side guide part (12, 13) ) in a partial area of the printing area or in the entire printing area, and the connecting channel (55) connects the interior (47) of the housing (2) containing the pressure (pA) to the outlet, characterized,
that the one side guide part (12, 13) through a control disk (12a, 13a) with control openings (32a, 32b) forming feed openings and the other side guide part (12,13) through a control disk (12a, 13a) with control openings (32a, 13a) 32b) is formed. Hydraulic machine (1) of the toothed ring type, in particular hydraulic motor, consisting of a housing (2), a shaft (3) rotatably mounted in the interior of the housing (2), which penetrates the wall of the housing (2) in a hole in a sealed manner with at least one shaft end, a rotor (5) arranged in the housing (2) in a rotationally fixed manner on the shaft (3) and having external teeth (6), a rotor ring (7) surrounding the rotor (5) with an internal toothing (8) which interacts with the external toothing (6) of the rotor (5), the rotor (5) and the rotor ring (7) being guided between lateral guide surfaces of lateral guide parts (12, 13), working chambers are formed between the toothings (6, 8) of the rotor (5) and the rotor ring (7) and form supply chambers and discharge chambers in opposite zones, which correspond to pressure supply and discharge openings of supply and discharge lines in rotation, which are connected to an inlet and to an outlet, the side guide parts (12, 13) are each mounted in a recess (19, 21) in the housing (2), one or both side guide parts (12, 13) being axially displaceably mounted in the interior of the housing (2) and acted upon by the hydraulic pressure (p1) and by a spring force against the rotor (5) and the rotor ring (7) and form a first pressure control device (49), A second pressure control device (54) with at least one control opening (54a) is provided in a connecting channel (55) for setting an approximately constant pressure difference between the working pressure (pA) and the pressure (p1.) applied to the axially displaceable side guide part (12, 13) ) in a partial area of the printing area or in the entire printing area, and the connecting channel (55) connects the interior (47) of the housing (2) containing the pressure (pA) to the outlet, or hydraulic machine according to claim 1 or 2, characterized,
that two or more second pressure control devices (54,54.A; 54.1,54.2,54.3,54.4) are provided in parallel, each of which controls a different pressure difference. Hydraulic machine (1) of the toothed ring type, in particular hydraulic motor, consisting of a housing (2), a shaft (3) rotatably mounted in the interior of the housing (2), which penetrates the wall of the housing (2) in a hole in a sealed manner with at least one shaft end, a rotor (5) arranged in the housing (2) in a rotationally fixed manner on the shaft (3) and having external teeth (6), a rotor ring (7) surrounding the rotor (5) with an internal toothing (8) which interacts with the external toothing (6) of the rotor (5), the rotor (5) and the rotor ring (7) being guided between lateral guide surfaces of lateral guide parts (12, 13), working chambers are formed between the toothings (6, 8) of the rotor (5) and the rotor ring (7) and form supply chambers and discharge chambers in opposite zones, which correspond to feed and discharge openings of feed and discharge lines in rotary operation, which are connected to an inlet and to an outlet, or hydraulic machine according to one of the preceding claims, characterized,
that several inlets (42 to 43) are provided, of which at least two inlets have differently sized flow channel cross sections or throttle cross sections (39, 41) and / or at the same time are connected or connectable to a supply line (Z) for the hydraulic pressure medium, and that they are not inlets connected or connectable to the feed line (Z) are closed. Hydraulic machine according to claim 1 or 4,
characterized
that one or both side guide parts (12, 13) or control disks (12a, 13a) are mounted axially displaceably in the interior of the housing (2) and acted upon by the hydraulic pressure and by a spring force against the rotor (5) and the rotor ring (7) is and are and form a first pressure control device (49). Hydraulic machine according to claim 5,
characterized,
that a second pressure control device (54) with at least one control opening (54a) is provided in a connecting channel (55) for setting an approximately constant pressure difference between the working pressure (pA) and the pressure present at the axially displaceable side guide part (12, 13) ) in at least a partial area of the pressure area, the connecting channel (55) connecting the interior (27) of the housing (2) containing the pressure (p1) to the outlet. Hydraulic machine according to one of the preceding claims,
characterized,
that the second pressure control device (54) is formed by a check valve which opens in the flow direction towards the outlet. Hydraulic machine according to one of claims 3 to 7,
characterized,
that the cross-sectional sizes of the control openings (54a) or the valve seat openings and / or the preloads of the valves (54b) of the further second pressure control device or devices (54) are different, in particular the cross-sectional sizes smaller and / or the voltages larger. Hydraulic machine according to one of claims 1 and 3 to 8,
characterized,
that on the one hand the pressure openings and on the other hand the return openings in the side guide parts (12, 13) are axially opposite one another. Hydraulic machine according to one of the preceding claims, characterized in that
that one or both round side guide parts (12, 13) is or are each held against rotation by a rotation lock device (20). Hydraulic machine according to claim 10,
characterized,
that the anti-rotation device (20) is arranged symmetrically to the control opening (s) adjacent to it (32a, 32b). Hydraulic machine according to one of the preceding claims, characterized in that
that the control discs (12a, 13a) are identical. Hydraulic machine according to one of the preceding claims,
characterized,
that at least one section of the connection channel (55) of the second pressure control device (54) containing the pressure control opening (54b) or the connection channel (55) is arranged overall in a component delimiting the feed chambers (29) in the housing (2) or in the housing (2) . Hydraulic machine according to one of the preceding claims, characterized in that
that the section of the connecting channel (55) containing the pressure control opening (54a) is arranged in the side guide part (control disk 12) containing the discharge lines (55, 36). Hydraulic machine according to one of the preceding claims,
characterized,
that the connecting channel (55) is connected downstream of the pressure control opening (54a) to a discharge line (36) or to a collecting line which connects the discharge lines (36). Hydraulic machine according to one of claims 13 to 15, characterized in that
that the connecting channel (55) extends approximately radially through the joint between the lateral guide part (12, 13) and the housing (2). Hydraulic machine according to one of the preceding claims,
characterized in that the connecting channel (55) in the lateral guide part (12, 13) is connected to a discharge line (36) or to a collective discharge line. Hydraulic machine according to one of the preceding claims,
characterized,
that the control openings (32a, 32b) forming the feed and / or discharge openings are each connected to a circumferential groove (37, 38) in the control disk (12a, 13a), from which a channel section (39, 41) preferably forming a throttle is formed extends to the associated inlet or outlet (42, 43). Hydraulic machine according to one of the preceding claims,
characterized,
that the connecting channel (55) opens into a circumferential groove (37a, 37b, 38a, 38b) of the side guide part (12, 13), from which a channel (39, 41) extends to the outlet in the housing (2), and that preferably a common circumferential groove (37a, 37b, 38a, 38b) is provided for the connecting channel (55) and the return lines (36). Hydraulic machine according to one of the preceding claims,
characterized,
that the second pressure control device (54) is arranged in a channel (56b) which preferably extends axially parallel in the side guide part (12, 13). Hydraulic machine according to one of the preceding claims, characterized in that
that the outlet or the outlets, with clockwise / counterclockwise rotation of the respective inlet and outlet, each has a bypass (62) with a check valve (61) in the form of a check valve which blocks the bypass (62) in the input direction and in the Exit direction opens. Hydraulic machine according to one of the preceding claims,
characterized,
that the bypass channel extends from the circumferential groove (37, 38). Hydraulic machine according to one of the previous claims,
characterized,
that the second or further pressure control devices (54, 54.1) are each formed by a check valve (54c). Hydraulic machine according to claim 24,
characterized,
that the valve (54b) is arranged in a stepped bore (55, 66). Hydraulic machine according to one of the preceding claims,
characterized,
that on both sides of the rotor ring (7) one or more inlets (A1, A2, A3, A4, A5, A6) offset in the circumferential direction and one or more outlets (A1, A2, A3, A4, A5, offset in the circumferential direction) A6) are provided on the housing (2). Hydraulic machine according to one of the preceding claims,
characterized,
that one or more inlets and / or outlets (A1, A2, A5) are arranged offset to one another in the circumferential direction on one side of the rotor ring (7) (FIG. 9).

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