FLUID MACHINE, ESPECIALLY HYDROMACHINE

Description

[0001] The invention relates to a fluid machine, in particular a hydraulic machine, which comprises at least one working chamber, wherein a rotor is rotatable by a torque or by a fluid which, for the operation of the machine, flows into the at least one working chamber on an inlet side and out of the at least one working chamber on an outlet side, wherein a rotation of the rotor effects a control of at least one valve.

[0002] WO 86 / 04683 A1 describes a fluid machine in which several valve disks form an inlet and outlet valve on an inlet and outlet side. Each of the valves comprises a first valve plate with several inlet and outlet openings through which the fluid can flow into and out of working chambers, and two further concentric valve plates, of which a first valve plate is fixedly arranged and a second valve plate is non-rotatably connected to a shaft of the fluid machine. The working chambers are formed between a stationary ring gear and a rotor ring gear, as well as between the rotor ring gear and a ring gear, and are located in the flow direction between the inlet and outlet valves.

[0003] From WO 2015 / 076716 A1, a fluid machine designed as a motor or pump is known in which a rotation of a shaft is achieved by a linear movement of "pistons" against external teeth ("cam profile") of a rotor shaft attachment.

[0004] US 4,697,997 A discloses a fluid machine in which a shaft can rotate about central axes A, B by means of spline connectors when a fluid is introduced.

[0005] Fluid machines designed either as drives or as pumps are also known from the prior art. Such fluid machines can be operated with a pressurized gas or a pressurized liquid such as water or oil.

[0006] Hydraulic machines powered by hydraulic oil are used, for example, as drives in construction vehicles and are characterized by particularly high drive torque. The hydraulic oil flows into a typically cylindrical machine housing, in which a rotor is located, from an inlet side, often referred to as the high-pressure side, through a working chamber to an outlet side, often referred to as the low-pressure side, causing the rotor to rotate to generate the drive torque.

[0007] There is an inlet valve on the inlet side and an outlet valve on the outlet side, which must open and close synchronously for the fluid machine to operate. For this purpose, conventional fluid machines require regulated valve control by a separate control unit to prevent pressure loss or unwanted fluid flow past the working chamber. This creates a structurally complex system that is also very maintenance-intensive.

[0008] The present invention is based on the object of developing a fluid machine of the type mentioned at the outset which does not require any sealing means and is therefore of particularly simple construction.

[0009] According to the invention, the object is achieved in that a through-channel through which the fluid can flow into the at least one working chamber through an inlet valve is delimited by eccentric valve discs and an inner wall of a machine housing or an inner machine housing.

[0010] Advantageously, it is ensured that the fluid can flow into the at least one working chamber on an inlet side, and a loss flow, i.e., a fluid flow that does not contribute to generating rotation of the rotor, is minimized. Furthermore, a fluid machine with a simple design is created, eliminating the need for special sealing means known from the prior art.

[0011] The valves are controlled directly and synchronously by the movement of the rotor. An additional control unit for controlling at least one valve is advantageously not required.

[0012] Conveniently, the at least one valve comprises at least one eccentric valve disc. The valve disc is preferably circular.

[0013] Because the preferably circular valve disc is arranged eccentrically, a gap forming a through-channel for the fluid is present between the disc and an inner wall of a cylindrical machine housing of the fluid machine, through which gap the fluid can flow into the at least one working chamber to operate the machine, while the valve disc forms a sealing surface with the machine housing on a side opposite the gap. The fluid can flow through the gap into the at least one working chamber and cause the rotor to rotate. For this purpose, fluid pressure acts on at least one outer rotor tooth of the rotor or at least one rotor shaft attachment tooth. A rotor shaft attachment is preferably attached eccentrically to a rotor shaft of the rotor by a tooth connection.

[0014] Adjacent rotor outer teeth or rotor shaft attachment teeth, a machine housing and at least one valve delimit the at least one working chamber.

[0015] If two eccentric valves are provided, one can control an inlet into the at least one working chamber, and another can control an outlet from the at least one working chamber. For this purpose, both the inlet and outlet valves can have at least one valve disc, with the at least one valve disc of the inlet valve being arranged, for example, offset by 90 degrees in the circumferential direction from the at least one valve disc of the outlet valve.

[0016] Because the at least one working chamber is defined by a machine housing, rotor outer teeth or rotor shaft attachment teeth, and the two valves, a force acting on the rotor outer teeth or rotor shaft attachment teeth due to fluid pressure can cause the rotor to rotate in such a way that an inlet opening of the at least one working chamber is reduced in size while an outlet opening is enlarged. This advantageously ensures that the fluid can flow into the at least one working chamber on the inlet side and out of the working chamber on the outlet side.

[0017] If the valve discs are connected to the rotor shaft or the rotor shaft attachment, the valve discs can move synchronously with the rotation of the rotor. Separate control, for example, by a control unit, is not required.

[0018] The valve discs can be elastic, for example, made of a plastic. This allows for adaptation to pressure-induced deformation of a machine housing during operation of the fluid machine. This advantageously prevents the formation of further gaps and the increase of leakage flow, i.e., fluid flow that does not contribute to generating rotor rotation.

[0019] In one embodiment of the invention, the plurality of eccentric valve discs are arranged one behind the other in a longitudinal direction of the rotor shaft, with adjacent valve discs being offset from one another, particularly in the circumferential direction. This offset arrangement advantageously ensures particularly good sealing of a working chamber during machine operation. Gaps that could cause flow through the at least one working chamber without generating torque are advantageously not formed. Leakage flow is minimized. The efficiency of the machine increases. Furthermore, leakage flow decreases with an increasing number of valve discs.

[0020] There are two valves, one on the intake side and one on the exhaust side, each of which comprises several valve discs.

[0021] In a further embodiment of the invention, the plurality of eccentric valve discs of the at least one valve are toothed and arranged one behind the other in a longitudinal direction of the rotor, with adjacent valve discs being offset from one another, particularly in the circumferential direction. Advantageously, the at least one valve is formed from identical components. This simplifies the manufacture of the fluid machine. The offset arrangement also advantageously ensures particularly good sealing of the working chamber during machine operation.

[0022] In one embodiment of the invention, valve discs of the at least one valve, the rotor, and / or a rotor shaft attachment are toothed. External teeth can be integrally formed on a rotor shaft of the rotor or a rotor shaft attachment. This advantageously simplifies the manufacture of the fluid machine. Essentially identical components can be used for both the valves and the rotor shaft attachment.

[0023] In a further embodiment of the invention, a machine housing of the fluid machine comprises a plurality of internal teeth, each of which is designed as a rotatable cylindrical element whose axis of rotation is preferably parallel to a longitudinal axis of the rotor. A working chamber is formed between adjacent rotor teeth or rotor shaft attachment teeth, adjacent internal teeth of the machine housing, and the inlet and outlet valves. External teeth of the valve discs, the rotor, or the rotor shaft attachment bear against the internal teeth, forming a sealing surface and moving relative to the internal teeth during machine operation as the rotor rotates and synchronously drives the valve discs. Friction losses are advantageously minimized by rotatably mounting the internal teeth. Efficiency increases and wear decreases.

[0024] Furthermore, the torque required to start the fluid machine is significantly lower than without rotatable bearings of the internal teeth.

[0025] It is also conceivable that valve discs of the at least one valve are provided with external teeth having rotatable cylinder elements, while internal teeth of a machine housing are rigid.

[0026] In one embodiment of the invention, a gap is formed between the cylinder element and the machine housing or an internal part of the machine housing. This gap is intended to receive fluid during operation of the fluid machine and acts as a lubrication pocket. Friction losses are advantageously further reduced. Furthermore, wear is reduced. By introducing a fluid under pressure on a high-pressure side (= inlet side), self-lubrication can occur during operation of the fluid machine. Fluid pressure during operation is used to fill the gap.

[0027] Advantageously, the at least one valve and the rotor are directly coupled to one another and rotatable synchronously. For example, the at least one valve can be connected to a rotor shaft in a rotationally fixed manner.

[0028] A positive connection is conceivable, in which the valve has internal teeth that mesh with external teeth of the rotor shaft. Rotation of the rotor relative to the rotor shaft attachment advantageously results in synchronous valve control. A separate control unit for controlling the valves is not required.

[0029] A material and / or frictional connection or a combination of different connection types is also conceivable.

[0030] In one embodiment of the invention, two valves are provided, a first of which regulates a fluid inlet into the at least one working chamber, and a second of which regulates a fluid outlet from the at least one working chamber. Both valves can be formed from at least one valve disc and connected in a rotationally fixed manner to a rotor shaft. It is understood that both valves are moved synchronously with the rotation of the rotor. This advantageously achieves self-regulation of the valve control.

[0031] It is conceivable that at least one valve disc of each valve rotates synchronously with a rotor shaft attachment of the rotor. The rotor shaft attachment preferably encloses a rotor shaft and is connected to it by a gear connection acting as a transmission. A gear ratio can be adjusted by selecting a suitable gearing. Advantageously, the rotor speed can be adjusted during operation of the fluid machine.

[0032] Although it is conceivable for an inlet and an outlet channel to be different sizes, in one embodiment of the invention, an inlet and an outlet channel are of equal size and, in particular, have identical cross-sections. This advantageously enables particularly simple manufacturing.

[0033] In one embodiment of the invention, the direction of rotation of the fluid machine is reversible by swapping a high-pressure and a low-pressure side. The high-pressure side is an inlet side, and the low-pressure side is an outlet side. Four-quadrant operation is advantageously possible.

[0034] The fluid flow into the fluid machine is preferably parallel, perpendicular, or oblique to the longitudinal direction of the rotor. This advantageously allows for considerable design freedom. There are no structural restrictions. Flexible use, for example, in vehicles of different sizes and for different applications is possible.

[0035] In a particular embodiment of the invention, the rotor is designed as a hollow shaft. Advantageously, the fluid machine can be designed as a ring that encloses a component to be rotated or is connected in a rotationally fixed manner to a component or assembly. Such a component or assembly can be the members of an industrial robot that are movable relative to one another and must exert particularly large forces.

[0036] Use in wind turbines is also conceivable.

[0037] In a further embodiment of the invention, the fluid machine is designed as a pump or as a drive. By rotating the rotor under an applied torque, a fluid can be transported from an inlet side to an outlet side. However, if a fluid flows under pressure from an inlet to an outlet side, the rotation of the rotor generates a torque that can be used, for example, to operate a drive train. Advantageously, the fluid machine can be used flexibly for various applications.

[0038] The invention is explained in more detail below with reference to exemplary embodiments and the accompanying drawings relating to the exemplary embodiments. They show: Fig. 1 shows a first embodiment of a fluid machine according to the invention in several views, Fig. 2 shows a second embodiment of a fluid machine according to the invention in several views, Fig. 3 shows a further embodiment of a fluid machine according to the invention in several views, Fig. 4 shows details of a special embodiment of a fluid machine which does not fall under the subject matter of the claim.

[0039] One in Fig. 1a in a partially sectioned isometric view, in Fig. 1b in a partially sectioned side view and in Fig. 1c The water-operated hydraulic machine (1) shown along a section BB comprises a cylindrical machine housing (2) in which a cylindrical rotor (3) is rotatably mounted by ball bearings (4).

[0040] The machine housing (2) is divided into an inlet chamber (13), several circumferentially arranged working chambers (14), and an outlet chamber (15) by a rotor shaft (5), on whose outer surface circumferentially spaced rotor outer teeth (6) are formed, two support discs (7, 8), and two valves (9, 10), each comprising a valve disc (11, 12). Each working chamber (14) is delimited by the valve discs (11, 12), adjacent rotor outer teeth (6), and the machine housing (2).

[0041] The two valve discs (11, 12) are arranged eccentrically on the rotor shaft (5) and offset from one another by 180° in the circumferential direction. A first through-channel (16) is formed between the valve disc (11) and the machine housing (2), through which water can flow from the inlet chamber (13) into several working chambers (14). A second through-channel (17) is formed between the valve disc (12) and the machine housing (2), through which water can flow from the working chambers (14) into the outlet chamber (15). The first (16) and the second through-channel (17) are located on opposite sides of the machine housing (2) and each extend over half its circumference.

[0042] The two support discs (7, 8) have a smaller diameter than the machine housing (2), so that an annular gap (18, 19) is formed between the support discs (7, 8) and the machine housing (2).

[0043] The support discs (7, 8), the rotor outer teeth (6) and the valve discs (11, 12) form sealing surfaces at the contact surfaces where they abut one another. Tightness is achieved by pressing these components against one another, by means of a Fig. 1b The thrust washer (21) shown in detail and a disc spring (22) are clamped in place. On one outlet side, the support disc (8) rests against another retaining ring (23).

[0044] During operation of the hydraulic machine (1), water can flow from a high-pressure side, which is an inlet side, through an inlet opening (24) into the inlet chamber (13) and through the annular gap (18) and the first through-channel (16) into the at least partially open working chambers (14). From the working chambers (14), the water can flow on the outlet side, with the valve disc (12) in a corresponding position, through the second through-channel (17) and the annular gap (19) into the outlet chamber (15) on the low-pressure side and out of the latter through an outlet opening (25) out of the machine housing (2).

[0045] Because the valve discs (11, 12) are arranged offset by 180 degrees from one another in the circumferential direction, the water flows into the working chambers (14) on the inlet side depending on the position of the valve disc (11), but cannot flow out on the outlet side, or only in small quantities, because the second through-channel (17) is blocked by the outlet-side valve disc (12). Water pressure is present at the outer rotor teeth (6) delimiting the working chambers (14), causing the rotor shaft (3) to rotate in the direction of an arrow (26). The valve discs (11, 12) attached to the rotor shaft (5) are rotated synchronously in such a way that, as the rotor rotates, the working chambers (14) are gradually closed on the inlet side and gradually opened on the outlet side. As a result, water that has flowed into the working chambers and causes the rotor to rotate is expelled on the outlet side.During a subsequent inflow and outflow cycle, with the valve discs (11, 12) positioned accordingly, water can again flow into the working chamber on the inlet side, causing synchronous rotation of the rotor and the valves (9, 10), and flow out on the outlet side. Continuous operation of the hydraulic machine (1) is possible.

[0046] In a Fig. 1c In the machine housing (2) shown, the rotor shaft attachment (6) is shown hatched. Water can flow directly from the inlet chamber (14) into the outlet chamber (15) through a section (27) of the through-channel (17).

[0047] It will now Fig. 2 Reference is made where identical or equivalent parts are identified by the same reference number as in Fig. 1 and the relevant reference number is followed by the letter a.

[0048] One in Fig. 2a in a partially cut isometric view, in Fig. 2b in a partially sectioned side view and in Fig. 2c The hydromachine (1a) shown along a section BB differs from the one in Fig. 1 shown in that each valve (9a, 10a) has three eccentric valve discs (28-30, 31-33) arranged one behind the other, which are arranged offset by 45 degrees from one another in the circumferential direction.

[0049] One in Fig. 2c shown, second through-channel (17a) has no Fig. 1 with (27) designated section with a gap between the valve discs (31-33) and a machine housing (2a), through which water can flow directly from an inlet chamber (13a) into an outlet chamber (15a) during operation of the hydraulic machine (1a).

[0050] A leakage flow directly from an inlet chamber (13a) to an outlet chamber (15a) is prevented or at least significantly reduced. The efficiency of the hydraulic machine (1a) is advantageously increased.

[0051] It will now Fig. 3 Reference is made where identical or equivalent parts are identified by the same reference number as in Fig. 1 and 2 and the relevant reference number is followed by the letter b.

[0052] One in Fig. 3a in a partial longitudinal section and in Fig. 3b A further embodiment of a hydraulic machine (1b), shown in a partial cross-section along BB, comprises a two-part, cylindrical machine housing (2b) having an outer machine housing (34) and an inner machine housing (35), wherein the inner housing (35) is provided with 18 internal teeth (36) intended to engage with 17 external teeth (37) of seven identical valve discs (38) of an inlet (9b) and an outlet valve (10b), as well as rotor shaft attachment teeth (6b) of a rotor shaft attachment (39). Each internal tooth is designed as a pin-like cylinder element (40) arranged in a bore (41) in the inner housing (35) that is partially open in the circumferential direction. Each cylinder element (40) is rotatable about an axis that is parallel to a longitudinal axis of the rotor (3b).

[0053] Between the cylinder elements (40) and the inner machine housing a Fig. 3 not shown gap is formed, which is intended to be filled with water during operation of the hydraulic machine (1b) and thus to act as a lubrication pocket.

[0054] Each of the seven valve discs (38) of each valve (9b, 10b) is arranged eccentrically to a cylinder axis of the machine housing (2b), wherein inner teeth (42) of the eccentric valve discs engage in outer teeth (43) of a rotor (3b) and adjacent valve discs (38) as in Fig. 3c und d shown in a partially sectioned isometric view, arranged offset from one another in the circumferential direction.

[0055] The rotor shaft attachment (39), which is eccentrically attached to the rotor shaft (5b) by a toothed connection, also has internal teeth (44) which engage with the external teeth (43) of the rotor (3b).

[0056] The valve discs (38) and the rotor shaft attachment (39) have substantially identical cross-sections, which means in particular that each valve disc (38) and the rotor shaft attachment (39) are provided with the same number of external teeth (37, 6b).

[0057] Working chambers (14b) are delimited by the valves (9b, 10b), adjacent cylinder elements (40), adjacent rotor shaft attachment teeth (6b) and the machine inner housing (35).

[0058] A fluid pressure when the fluid, which can be water, oil or a gas, flows into the working chambers (14b) against the rotor shaft attachment teeth (6b) and causes a rotation of the rotor shaft attachment (39), which, through its tooth connection with the valve discs (38) and the rotor shaft (5b), causes a control of the valves (9b, 10b) synchronous to the rotational movement.

[0059] The fact that the valve discs (38) are circumferentially offset from one another and arranged eccentrically ensures that fluid can flow into the working chambers on the inlet side and out of the outlet side after further rotation of the rotor (3b) during operation of the fluid machine (1b). Loss of flow is completely prevented. The synchronous movement of the valve discs (38) advantageously enables continuous operation.

[0060] It will now Fig. 4 Reference is made where identical or equivalent parts are identified by the same reference number as in Fig. 1 bis 3 and the relevant reference number is followed by the letter c.

[0061] A detail of a Fig. 4a in an isometric rear view and in Fig. 4b A special embodiment of a hydraulic machine (1c) shown schematically in a plan view, which does not fall under the subject matter of the claim, comprises a rotor shaft attachment (39c) with seventeen rotor shaft attachment teeth (6c) and a machine housing inner part (45) which is arranged in a Fig. 4 not shown hollow cylindrical machine housing, in the outer surface of which bores are made through which a fluid, which may be water, oil or a gas, can flow into inlet channels (46) and out through outlet channels (47). Each inlet (46) and outlet channel (47), which are of equal size, extends perpendicular to a Fig. 4 rotor shaft (not shown). Both channels (46, 47) can be at least partially opened or closed simultaneously by a single rotatable valve (48), since a semi-cylindrical valve body (49) of the valve (48) extends over both channels (46, 47).

[0062] On one end face, each of the valve bodies (49) has an eccentric actuating pin (50), the actuation of which causes rotation in different directions. Fig. 4a shown valve positions are possible.

[0063] Each actuating pin (50) engages in blind holes formed and in Fig. 4c schematically shown holes (51). In an annular groove (52) of a control disc (53) engages a Fig. 4c A circumferentially extending web (not shown) is formed integrally with a rotor shaft attachment (39c). As a result, the control disc (52) and a rotor (3c) move synchronously during machine operation, thereby controlling the valves (48).

[0064] A working chamber (14c) is defined by adjacent rotor shaft attachment teeth (6c), adjacent cylinder elements (40c), the associated semi-cylindrical valve body (49) and the control disc (53). On a side opposite the control disc, a Fig. 4 cover not shown is provided.

[0065] If a fluid flows through the inlet channels (46) into one of the working chambers (14c), the rotor (3c) and the control disc (53) rotate synchronously, changing the position of the semi-cylindrical valve bodies (49) so that previously closed valves are at least partially opened and open ones are at least partially closed. As a result, a fluid pressure acting against the rotor's external teeth (6c) can cause rotation of the rotor (3b) and synchronous movement of the valves (48). Continuous operation of the hydraulic machine (1c) is possible.

[0066] Although in Fig. 4 not shown, it is conceivable that each valve (48) comprises a two-part valve body, the first valve body part of which is rotatable by a first control disc (53), and the second valve body part of which is rotatable by a Fig. 4 A second control disc of identical construction, not shown. The second control disc can be mounted on a side opposite the first control discs and can preferably be formed integrally.

[0067] Furthermore, it is conceivable that each toothed valve disc (38) is provided with external teeth (37), each of which is designed as a rotatable cylinder element (40; 40c), while internal teeth of a machine housing (2b) or of a machine housing inner part (45) are designed to be fixed.

[0068] It is understood that all combinations of features of the Fig. 1 bis 4 shown embodiments are conceivable.

[0069] It is also conceivable that a fluid machine (1-1b) according to the invention is designed as a pump and / or is operated with oil or a gas such as nitrogen.

Claims

1. Fluid machine (1; 1a; 1b), in particular hydraulic machine, comprising at least one working chamber (14; 14a; 14b), wherein a rotor (3; 3a; 3b) is rotatable by a torque or by a fluid that flows into the at least one working chamber (14; 14a; 14b) on an inlet side and out of the at least one working chamber on an outlet side in order to operate the machine, wherein a rotation of the rotor (3; 3a) causes at least one valve (9, 10; 9a, 10a; 9b, 10b) to be controlled, characterized in that a passage channel (16-16b), through which the fluid can flow into the at least one working chamber (14-14b) via an inlet valve (9; 9a), is bounded by eccentric valve discs (11, 12; 28-30, 31-33; 38) and by an inner wall of a machine housing (2; 2a) or of an inner machine housing (35).

2. Fluid machine according to claim 1, characterized in that the plurality of eccentric valve discs (11, 12; 28-30, 31-33; 38) are arranged one behind the other in a longitudinal direction of the rotor (3; 3a), wherein adjacent valve discs (11, 12; 28-30, 31-33; 38) are arranged offset to one another, in particular in a circumferential direction.

3. Fluid machine according to claim 1 or 2, characterized in that the plurality of eccentric valve discs of the at least one valve (9b, 10b) are toothed and arranged one behind the other in a longitudinal direction of the rotor (3b), adjacent valve discs (38) being in particular arranged offset relative to one another in a circumferential direction.

4. Fluid machine according to one of claims 1 to 3, characterized in that valve discs (38) of the at least one valve (9b, 10b), the rotor (3b) and / or a rotor shaft attachment (39) are toothed.

5. Fluid machine according to one of claims 1 to 4, characterized in that a machine housing of the fluid machine comprises a plurality of internal teeth (36; 36c), each of which is configured as a rotatable cylinder element (40), the axis of rotation of which is preferably parallel to a longitudinal axis of the rotor.

6. Fluid machine according to claim 5, characterized in that a gap is formed between the cylinder element (40) and the machine housing (2b) or a machine housing inner part (45), which gap is provided for receiving fluid during operation of the fluid machine and acts as a lubrication pocket.

7. Fluid machine according to one of claims 1 to 6, characterized in that the at least one valve (9, 10; 9a, 10a; 9b, 10b) and the rotor (3; 3a) are directly coupled to one another and are synchronously rotatable.

8. Fluid machine according to one of claims 1 to 7, characterized in that two valves (9, 10; 9a, 10a; 9b, 10b) are provided, of which a first valve (9; 9a; 9b) controls a fluid inlet into the at least one working chamber (14; 14a; 14b) and a second valve (10; 10a; 10b) controls a fluid outlet from the at least one working chamber (14; 14a; 14b).

9. Fluid machine according to one of claims 1 to 8, characterized in that a direction of rotation of the fluid machine is reversible by exchanging a high-pressure side and a low-pressure side.