Electro hydrostatic actuators

Abstract

An electro hydrostatic actuator (EHA) comprises a hydraulic pump and an electric motor driving the hydraulic pump. The hydraulic pump comprises an inlet and an outlet for hydraulic fluid and an active fluid flow path arranged therebetween such that, in an active mode of operation when the pump is driven by the electric motor, hydraulic fluid is actively drawn in through the inlet and exhausted out through the outlet. The hydraulic pump further comprises a bypass flow path arranged between the pump inlet and outlet, such that, in a damping mode of operation, hydraulic fluid is able to freely flow between the inlet and outlet in either direction.

Claims

1. An electro hydrostatic actuator (EHA) comprising: electric motor; and a hydraulic pump driven by the electric motor, the hydraulic pump to supply hydraulic fluid to a hydraulic actuator, the hydraulic pump comprising: an inlet and an outlet for hydraulic fluid and an active fluid flow path arranged therebetween such that, in an active mode of operation when the pump is driven by the electric motor, hydraulic fluid is actively drawn in through the inlet and exhausted out through the outlet; and a bypass flow path arranged between the pump inlet and outlet, such that, in a damping mode of operation, hydraulic fluid is able to freely flow between the inlet and outlet in either direction; wherein the electric motor comprises: a moveable member arranged to move within the motor such that, when the motor is energised so as to drive the pump in the active mode of operation, the member has a blocking position that acts to block the bypass flow path, and when the motor is not energised the member moves within the motor to open the bypass flow path in the damping mode of operation.

2. An electro hydrostatic actuator according to claim 1, wherein the moveable member is arranged to move axially within the motor to open the bypass flow path.

3. An electro hydrostatic actuator according to claim 1, wherein the member is moved automatically, to open the bypass flow path, when the pump is not driven by the electric motor.

4. An electro hydrostatic actuator according to claim 3, wherein the pump comprises a resilient member arranged to move the member and thereby open the bypass flow path when the pump is not driven by the electric motor.

5. An electro hydrostatic actuator according to claim 1, wherein the electric motor comprises an electromagnetic arrangement that holds the moveable member in the blocking position.

6. An electro hydrostatic actuator according to claim 5, wherein the electromagnetic arrangement comprises one or more additional coils arranged to magnetise the moveable member.

7. An electro hydrostatic actuator according to claim 1, wherein the size of the bypass flow path is adjusted during use of the pump to provide a desired damping factor for the hydraulic actuator.

8. An electro hydrostatic actuator according to claim 7, wherein the motor comprises a pin arranged to limit the position of the member when it moves to open the bypass flow path.

9. An electro hydrostatic actuator according to claim 1, comprising a sensor arranged to detect movement of the member to determine whether the bypass flow path is open.

10. An electro hydrostatic actuator according to claim 1, wherein the hydraulic pump is a rotary piston pump comprising a pump barrel driven to rotate by a motor shaft and a plurality of axial cylinders in the pump barrel arranged to receive reciprocating pistons, wherein the inlet has a fluid connection with the axial cylinders in one half of the pump barrel and the outlet has a fluid connection with the axial cylinders in the other half of the pump barrel.

11. An electro hydrostatic actuator according to claim 10, wherein the bypass flow path comprises one or more connecting ports in the pump barrel that provide a direct fluid path, in the damping mode of operation, between the inlet connected to axial cylinders in one half of the pump barrel and the outlet connected to the axial cylinders in the other half of the pump barrel, wherein the member is arranged in the motor shaft to have a position that blocks the flow of fluid through the connecting ports in the active mode of operation.

12. A method of controlling and damping a hydraulic actuator, comprising: energising an electric motor to drive a hydraulic pump to supply hydraulic fluid to the hydraulic actuator in an active mode of operation; and controlling movement of a moveable member arranged within the motor to open a bypass flow path through the hydraulic pump when the pump is not driven by the electric motor in a damping mode of operation.

13. A method according to claim 12, wherein controlling movement of the moveable member comprises energising one or more additional coils arranged to magnetise the moveable member.

14. A method according to claim 12, comprising adjusting the size of the bypass flow path during use of the pump to provide a desired damping factor for the hydraulic actuator.

15. A method according to claim 14, wherein adjusting the size of the bypass flow path comprises adjusting a pin that is arranged to limit the position of the moveable member when it moves to open the bypass flow path.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) One or more non-limiting examples will now be described with reference to the accompanying drawings, in which:

(2) FIG. 1 shows a fluid flow diagram for an EHA in an active mode according to the prior art;

(3) FIG. 2 shows a fluid flow diagram for an EHA in a damping mode according to the prior art;

(4) FIG. 3 shows a typical rotary piston pump;

(5) FIG. 4 shows the port plate of a typical rotary piston pump.

(6) FIG. 5 shows a fluid flow diagram for an EHA in an active mode according to the present disclosure;

(7) FIG. 6 shows a fluid flow diagram for an EHA in a damping mode according to the present disclosure;

(8) FIG. 7 shows an example of a pump where the bypass fluid flow path is blocked according to the present disclosure;

(9) FIG. 8 shows the pump of FIG. 7 where the bypass fluid flow path is open;

(10) FIG. 9 shows a cut-away view of the pump in the active mode where the bypass fluid flow path is blocked according to the present disclosure;

(11) FIG. 10 shows a view of the pump of FIG. 9 in the damping mode.

DETAILED DESCRIPTION OF THE INVENTION

(12) FIGS. 1 and 2 show a fluid flow diagram for an electro hydrostatic actuator (EHA) 2 according to the prior art. FIG. 1 shows a reversible electric motor 4, a hydraulic pump 6, a mode valve 8, an accumulator 10 and a hydraulic actuator 12. The hydraulic actuator 12 shown in FIG. 1 consists of two separate chambers 14, 16 and an actuator ram 18. The mode valve 8 can be operated by a solenoid 20 and has two modes of operation which is typically on or off. The ram 18 is typically attached to a component on the aircraft such as an aerodynamic surface. The EHA typically has two modes of operation: an Electric Active Mode (EAM) and a damping mode. FIG. 1 shows the EHA in EAM. During EAM the motor 4 acts to drive the pump 6. This can be in either direction as the pump 6 is reversible. As the pump 6 is driven it causes hydraulic fluid to flow around a circuit as shown by the bold lines and the arrows in FIG. 1. This results in fluid being directed into one of the chambers 14, 16 of the hydraulic actuator 12. As fluid enters one of the chambers 14, 16 and leaves the other chamber 14, 16 this causes the ram 18 to move within the chambers 14, 16 which acts to move the aerodynamic surface it is attached to.

(13) FIG. 2 shows a fluid flow diagram for the EHA 2 in damping mode. The damping mode can be initiated in circumstances where there is an electrical power generation failure or electronic control path failure. The solenoid 20 is capable of activating the mode valve 8 which alters the fluid flow within the system. The damping mode introduces a damping effect to the ram 18. This may be critical for certain applications of an EHA for example when in use on an aircraft. The damping mode is also the default mode when the ram 18 is not required to be engaged i.e. the pump 6 is not driven by the motor 4. The purpose of the damping mode is to provide a damping force to the ram 18 which may be connected to an aerodynamic surface, this prevents uncontrolled motion when external aerodynamic forces are applied to the surface. In the damping mode, fluid is free to flow between one chamber 14, 16 through the mode valve 8 and to the other chamber 14, 16 of the hydraulic actuator 12. The free flow of fluid between the two chambers 14, 16 acts to damp the motion of the ram 18. During the damping mode the fluid completely bypasses the pump 6 and only travels through the mode valve 8. The damping effect on the ram 18 is fixed by the mode valve 8.

(14) FIG. 3 shows a typical rotary piston pump 22 operated by a motor shaft 24. The motor shaft 24 drives a pump barrel 26 by the connection of splines on the circumference of the motor shaft (not shown) and corresponding splines (not shown) on the internal surface of the pump barrel 26. The splines typically have a one to one correspondence and thus there is minimal relative rotation between the motor shaft 24 and the pump barrel 26. Internal splines 28 on the rear end of the motor shaft 24 provide for connection between the motor shaft 24 and the motor itself (not shown). The pump 22 is comprised of a pump barrel 26 with axial cylinders 30 extending therethrough. The spacing of the axial cylinders 30 is equiangular with respect to the centre of the pump barrel 26. Pistons 32 are present within the axial cylinders 30 and are free to reciprocate within the cylinders 30. The pistons 32 are linked by shoes 34 to a rotating plate 36 guided by a cam plate 38. The cam plate 38 is orientated at an angle such that, at any moment in time, at one side the pistons 32 are fully inserted in the cylinders 30 and at the other side they are drawn out of the cylinders 30.

(15) During typical operation of the pump 22 the motor shaft 28, driven by a motor, drives the pump barrel 26 causing it to rotate. As the pump barrel 26 rotates the pistons 32 reciprocate within the axial cylinders 30 causing fluid to be drawn into the pump barrel 26 on one side and expelled on the opposite side of the barrel 26. Although the cam plate 38 is shown at a fixed angle, it may be adjustable to control the amount of fluid that is being displaced from the pump.

(16) FIG. 4 shows a view of the underside of the pump 22 and shows in detail the port plate 40 which is attached to the base of the pump barrel 26. On the port plate 40 are two ports 42 which provide access to the cylinders 30 of the pump barrel 26. The ports 42 are semi-circular and follow the same arc as the circumferential positioning of the cylinders 30 in the pump barrel 26. The purpose of the provision of two ports 42 with a spacing between them is to prevent fluid being drawn in from the expulsion side of the pump. The gap between the ports 42 effectively corresponds to the points of change in gradient on the cam plate 38 from a positive to negative gradient or negative to positive gradient. One port 42a acts as an inlet to the pump 22 while the other port 42b acts as an outlet, or vice versa.

(17) FIGS. 5 and 6 show exemplary fluid flow diagrams according to the present disclosure. Instead of the damping mode being achieved by having a mode valve separate to the pump, it is now provided by a bypass flow path 123 incorporated internally within the pump 106. FIG. 5 shows a motor 104 which is operatively connected to a pump 106. Within the pump 106 there is an incorporated bypass flow path 123. A moveable member within the motor 104, for example an axially moveable member, acts to block the bypass fluid flow path 123. The moveable member will be described with reference to later Figures. The bypass flow path 123 is opened by a spring 125. FIG. 5 shows the pump during typical operation. During active mode the motor 104 rotates to operate the pump 106 which drives fluid around the circuit 102 through the pump 106. The motor 104 also acts to physically block the bypass fluid flow path 123. The fluid can be driven to/from the chambers 114, 116 of the hydraulic actuator 112 via the fluid path shown in bold and with corresponding arrows. Also shown is a linear transducer 144 connected to the ram 18 to signal when the ram 18 is in use. An additional linear transducer 146 is also connected to the motor 104 to signal when the component within the motor is blocking/unblocking the bypass fluid flow path 123.

(18) FIG. 6 shows the pump 106 operating in damping mode. In damping mode the motor 104 is no longer energised and thus no longer drives the pump 106. In this damping mode the spring 125 acts to move the moveable member of the motor 104 which blocks the bypass fluid flow path such that it no longer acts to block the bypass fluid flow path 123. In this damping mode, fluid in each of the hydraulic actuator's chambers 114, 116 is free to flow along the bypass flow path 123, which is through the pump 106, to the other chamber 114, 116. This would not be possible in a typical piston pump as there is no means for the fluid to transfer from the cylinders on one side of the pump 106 to the other side. This is possible with the present disclosure and can be seen in the following Figures.

(19) FIGS. 7 and 8 show an EHA 102 comprising a motor 104, a pump 106 and a hydraulic actuator 112 in accordance with an example of the present disclosure. The EHA 102 comprises a pump 106 similar to the pump 22 shown in FIG. 3, however the EHA 102 utilises a one-part motor shaft 124 (i.e. no connecting splines 28). FIG. 7 shows the EHA 102 in an active mode. In the active mode the pump 106 is driven to rotate by the motor shaft 124. The motor shaft 124 passes from the motor 104, through the cam plate 138, to drive the pump barrel 126. The motor shaft 124 typically drives the pump barrel 126 by a series of splines 164 on the circumference of the motor shaft 124 (seen in FIGS. 9 and 10) and a series of corresponding splines on the internal region of the pump barrel 126. The motor shaft 124 has a hollow core through which passes an axial rod 148. The axial rod 148 has a lower disked shaped portion 150 at its lower end, proximal to the pump 106. The cylinders 130 in the pump barrel 126 have radial connecting ports 152 that lead towards a central internal cavity within the pump barrel 126. It is these connecting ports 152 that form the bypass flow path when they are open. The spring 125 is positioned in a recess in the core of the pump barrel 126. The disked shaped portion 150 is in contact with the spring 125 and acts to block central cavity and the connecting ports 152. The axial rod 148 effectively acts as a valve for the bypass flow path. This ensures that in the active mode fluid is only able to enter and leave the cylinders 130 by means of the inlet/outlet. In the active mode fluid is driven by the pump 106 into the respective chambers 114, 116 of the hydraulic actuator 112 which moves the ram 118.

(20) FIG. 7 also illustrates the key components of the motor 104. The motor 104 operates similar to a typical motor and utilises three standard drive coils 156 and permanent magnets to drive the motor shaft 124. Typically the motor is a brushless A.C. motor that uses an angle sensor and control electronics to commute the current in the appropriate coils. In the active mode an electric current is passed through the coils 156, the presence of an electric current in the coils 156 in a magnetic field present due to the permanent magnets, causes the coil/permanent magnets to experience a force and thus rotate. This rotation drives the motor shaft 124 causing it to rotate. The axial rod 148 extends through the motor shaft 124 into the main housing of the motor 104. The axial rod 148 also has a three further ferromagnetic disk shaped portions 154 housed within the motor 104.

(21) In series with the three drive coils 156 are three further valve coils 158. The three valve coils 158 pass annularly around the motor 104 housing. The three valve coils 158 are separated and positioned on the motor 104 proximal to the disk shaped portions 154 of the axial rod 148. Within the shaft 124 are three ferromagnetic rings 160. These annular ferromagnetic rings 160 pass annularly around the axial rod 148 and are fixed in place, each ferromagnetic ring 160 is positioned proximal to a corresponding ferromagnetic disk 154 of the axial rod 148. When a current is passed through the valve coils 158 an electromagnet is produced causing the ferromagnetic disked shaped portions 154 of the axial rod 148 to form magnetic poles. Each of the three ferromagnetic disk shaped portions 154 is subsequently attracted to its corresponding ferromagnetic rings 160. This causes the rod 148 to be held in a position with the each ferromagnetic disk portion 154 held against the corresponding ferromagnetic rings 160. The ferromagnetic disks 154 being held against the ferromagnetic rings 160 can be seen in the enlarged view shown on FIG. 7. The valve coils 158 are wired in series with the motor coils 156 such that when the motor coils 156 are energised the valve coils 158 are energised. The axial rod 148 will be held in this fixed position when the motor 104 is energised i.e. the EHA is in an active mode.

(22) When the axial rod 148 is held in position by the electromagnet established by the motor, this is the lower position causing the lower disk shaped portion 150 to be forced into a position blocking the connecting ports 152. In this lower position the force provided by the electromagnets has to overcome the resilient force provided by the spring 125. The lower disk 150 blocking the connecting ports 152 can also be seen in the enlarged view of the disk portion 150. In the active mode the resiliency of the spring 125 attempts to push the axial rod 148 upwards. However, due to the strength of the electromagnets established in the motor holding the axial rod 148 in position, the axial rod 148 is not able to move axially. In the example EHA shown in FIG. 7, in the active mode, the axial rod 148 rotates with the motor shaft 124. However, it is appreciated that in some examples the axial rod 148 may not rotate with the shaft 124 and instead may remain rotationally fixed.

(23) Also shown in FIG. 7 is the damping adjustment pin 162. This pin 162 can be used to control the amount of damping experienced by the hydraulic actuator 112. The pin 162 provides a limiting position preventing further movement of the axial rod 148 once it has moved into contact with the pin 162. This will be described in more detail with respect to FIG. 8.

(24) FIG. 8 shows the EHA 102 in the damping mode, in this mode the motor shaft 124 is not driven by the motor 104, i.e. the motor 104 is not energised. In this case both the drive coils 156 and valve coils 158 are not energised, therefore the motor shaft 124 does not rotate and the ferromagnetic disked shaped portions 154 are not transformed into electromagnets. In this mode the bypass flow path within the pump 106 is opened so that fluid can freely flow through between the chambers 114, 116 of the hydraulic actuator 112. In this damping mode the spring 125 acts to push on the disk 150 causing the axial rod 148 to move upwards. This causes the ferromagnetic disk shaped portions 154 to move away from the ferromagnetic rings 160. This can be seen in the enlarged view also shown in this FIGURE. This upward movement of lower disk 150 and the axial rod 148 opens the bypass fluid flow path. Arrows on the FIGURE show the free flow of fluid between the cylinders 130 in the pump barrel 126. This allows fluid to flow between the chambers 114, 116. In the example shown the spring 125 will partially extend into the bypass flow path. It is appreciated that this may have an impact on the damping factor and therefore in alternative examples it may be possible to arrange the spring such that it does not impact the bypass flow path.

(25) FIG. 8 also illustrates how the axial rod 148 moves to come into contact with the position limiting pin 162. The uppermost ferromagnetic disk portion 154 abuts against the position limiting pin 162 when the spring 125 acts to push the axial rod 148 upwards. The position limiting pin prevents the rod 148 from moving any further axially and thus impacts how far the lower disk 150 is able to move to open the bypass flow path. It is appreciated that the damping factor can be adjusted by causing more of the lower disk 150 to remain partially obstructing the bypass flow path, thus increasing the damping factor. In the example shown the position limiting pin 162 can be adjusted so as to adjust the damping factor. The pin 12 may be threaded or provided with any other suitable means to control its position. Using a position limiting pin 162 which is adjustable is particularly advantageous as the degree of damping can be adjusted after manufacture. This may be particularly useful if the EHA is used for different uses components which require different levels of damping.

(26) FIG. 9 shows a cut-away view of the pump 106 according to the present disclosure. The motor shaft 124 comprises a plurality of spines 164 which act to drive the pump barrel 126. This FIGURE shows the pump 106 in the active mode. In this mode it can be seen that the lower disk portion 150 at the base of the rod 148 is positioned such that the connecting ports 152 are blocked. It can be seen that the spring 125 is positioned in the core of the pump barrel 126. In the active mode the spring 125 is compressed by the axial rod and therefore acts to bias the axial rod 148 upwards. In this active mode the motor shaft 124 drives the pump barrel 126 to rotate, this causes the pistons 132 to reciprocate in the cylinders 130, subsequently causing fluid to be drawn in and expelled from the inlets and outlets 166.

(27) FIG. 10 shows a cut-away view of the pump 106 according to the present disclosure in the damping mode. In this mode the motor 104 is no longer energised and allowing the axial rod 148 to move axially within the drive shaft 124 and motor 104. In the damping mode the spring 125 is able to push the lower disk 150 upwards thus opening the bypass fluid flow path. Once the lower disk 150 has moved to open the connecting ports 152 it is possible for fluid to pass into the pump 106, through an inlet into a cylinder 130, pass through the connecting ports 152 and out of the outlet of a different cylinder 130. This allows the pump 106 to act in a damping mode.

(28) It is appreciated that in some examples, particularly those in which the axial rod 148 is able to rotate with the motor shaft 124, the clearance between the lower disk 150, the motor shaft 126 and connecting ports 152 must be designed to reduce the degree of leakage through the bypass fluid flow path in the active mode. Alternative there may be various additional features which could be incorporated to prevent leakage through the bypass flow path, for example, a rubber O-ring may be provided to seal the bypass fluid flow path.

(29) In the examples shown, when in the damping mode, the axial rod 148 is forced to open the bypass fluid flow path by a spring 125 positioned in the pump barrel 126. Although a single spring 125 is shown it is appreciated that there could be a plurality of springs which would achieve the same result. It is also appreciated that the means for moving the axial rod 126 may not necessarily be positioned in the pump barrel 126. For instance, a spring could be positioned anywhere along the motor shaft 124 and act against lugs on the axial rod 125 to force it move upwards. Furthermore, although a spring 125 is shown to move the axial rod it is appreciated that any other suitable means could be used, for example a series of magnets or an alternative resilient material could be used.

(30) In the examples shown three valve coils 158 are used to hold the axial rod 148 in a fixed position. It is appreciated that an alternative arrangement or a different number of coils could be used to achieve the same result. The positioning of the coils could be altered in order to hold the axial rod 148 at a different position. Furthermore in the example given the valve coils 158 are shown to be in series with the motor coils 156, it is appreciated that this may not be necessary and that the coils may be arranged, for example, in parallel. Additionally whilst in the example shown the valve coils are connected to the motor coils 156 it is appreciated that they may be part of a separate circuit with their own electronic control.

(31) The examples disclosed above relate to a rotary piston pump, but it will be appreciated that other types of pump may be used instead. Furthermore, although in the examples shown the angle of the cam plate is fixed, it is appreciated that changing the angle of the cam plate alters the amount of fluid drawn in and expelled by the pump, therefore it may be adjustable in order for the flow rate of fluid to be modified e.g. depending on the application of the pump.

(32) In the examples shown an axially moveable member 148 is provided in the motor shaft 126. However, it is appreciated that any other suitable member may be provided, for example, a member which is able to rotate in order to open the bypass flow path. For example, in one angular orientation the member might block the bypass flow path and in a second angular orientation it may open the bypass flow path.