Patent Application
20160177913
The invention relates to a device for controlling the displacement of a machine with variable displacement axial pistons.
In particular, the invention relates to a device for a machine that makes it possible to automatically switch between a small and a large displacement by a variation in the inclination of a plate, according to certain pressures.
Machines with axial pistons are machines that can operate either as a pump, or as an engine. For this (see
The inclination of the plate is variable in relation to a plane perpendicular to the axis of rotation R-R′ thanks to cylinders V1, V2 and makes it possible to adjust the travel of the pistons Q and therefore the displacement (see
The full machine integrates several elements. In a common case that comprises a cover, is located both the pump/engine structure BC, Q1, Q2, with the plate IP, and hydraulic means which make it possible on the one hand to control the arriving and the returning of oil to the pistons Q and on the other hand to control the inclination of the plate IP in order to vary the displacement.
These hydraulic means comprise two separate units S1 (controlling pressures), S2 (controlling of the plate) for these two functions, which use valves and complex connections.
However, these hydraulic means (and its two units) must be integrated into the case and in particular into the cover.
In reference to
As for the unit S2 for controlling the plate, it can be broken down into several embodiments: non-automatic and automatic switching.
The unit S2 comprises a five-port control valve and two positions which make it possible:
The controlling is carried out by a control pressure line Ps that is also independent.
In this embodiment, the controlling is controlled solely by the control pressure line Ps.
In
Document WO 2007/115828 describes such a device.
The unit S3 comprises a two-port valve one position in blocked position by default and controlled by a line that is piloted by the highest pressure of P1 et P2. The valve of the unit S3 comprises a pin, a spool and a spring that the pin can compress by driving the spool in translation. In conditions of light work, the pressure of the engine decreases and the hydraulic load of the oil that acts on the pin is less than the value of the spring. The spool becomes blocking and the circuits of two cylinders are no longer discharged via the unit S3 towards the tank. The pressure in these circuits then increases. The plate is displaced from its maximum displacement configuration to its minimum displacement configuration. Inversely, in difficult working conditions, the hydraulic load increases and the spool does not block. The oil of the cylinder circuits is then unloaded into the tank and the plate recovers its maximum displacement configuration.
Alternatively, as shown in
This unit S2′ comprises a case A1 that houses a control spool A2 that can be switched according to an axis of switching Δ between two positions by a control pressure Ps:
The spool A2 is maintained in idle position by a spring A3, connected to an end of the spool A2 and to a plug A4. The spring A3 exerts a force according to the axis Δ which tends to move the spool A2 away from the plug A4. The plug A4 closes the case in a sealed manner.
Furthermore, between the plug A4 and the spool A2 is located a cavity A5 which can receive the oil from the control pressure Ps. The oil under control pressure Ps exerts a force on the spool A2 collinear in the same direction as the spring A3.
The case A1 comprises an inlet of oil under pressure Pm on another end of the spool A2, which can exert a force on the spool, in the direction opposite that of the spring A3 exerted on the spool A2.
In this way, the displacement of the spool A2 depends on the pressures Pm, Ps and on the spring A3. In particular, when the force exerted by the pressure A6 is less than that exerted by the spring A3, the spool A2 is maintained in idle position. When this pressure increases, it makes it possible to displace the spool A2 by compressing the spring A3.
When the switching pressure Pm is activated, the positioning of the spool A2 is carried out automatically according to the value of this switching pressure Pm. However, it is not permitted to obtain a simple correspondence between the position of the spool A2 and the values of the pressures A6 and Ps.
Indeed, when the spring A3 is compressed to the maximum by the pressure Ps, the switching pressure Pm required to displace the spool A2 to its idle position will be less than that required to maintain the spool A2 in its idle position, due to the lengthening of the spring A3, which sees ipso facto its force decrease when its lengthening increases (spring maintained in compression).
This gives rise to problems with controlling the pressure and with adjusting the spool A2.
As such, regardless of the controlling unit S2 described hereinabove, none are fully satisfactory. The first substantially complicates and modifies the architecture of the pump in relation to so-called standard versions, and the second has problems in terms of control.
The invention proposes a device for controlling the displacement of a machine with axial pistons comprising a case that houses a control unit comprising:
The invention may also include the following features, taken alone or in combination:
The invention also relates to a machine with axial pistons comprising a device as described above, wherein the case comprises:
The invention may also include the following features, taken alone or in combination:
At last, the invention also relates to a method for using a device as described above, wherein:
a. If no control pressure is applied, then the control spool is maintained in idle position by the spring,
b. If a control pressure is applied then the change in displacement is automatically carried out according to the load applied to the machine,
i. If the force exerted by the control pressure is greater than the force exerted by the switching pressure, then the control spool is in working position,
ii. If the force exerted by the control pressure is less than the force exerted by the switching pressure, then the control spool is in idle position.
The method may also include the following features, taken alone or in combination:
Other characteristics, purposes and advantages of the invention shall appear in the following description, which is purely for the purposes of information and is not restricted, and which must be read in respect to the annexed drawings, wherein:
In reference to
The device 10 is a unit for controlling the plate S2, integrated into a machine with variable displacement axial pistons 20 through inclination of the plate. The device 10 is a selector arranged in a hydraulic circuit 30 (see
The device 1 has two positions: in an idle position, the two cylinder lines 31, 32 are emptied, in a working position, the two cylinder lines 31, 32 are pressurised.
A first supply line 33 connects a unit S1 for controlling the pressures to the pistons of the machine 20 and a second supply line 34 connects the pistons of the machine 20 to the unit S1. It is specified that the roles can be inverted according to the direction of operation of the machine (forward movement or backward movement). The supply lines 33, 34 are supplied at pressures P1, P2. A unit S1 for controlling pressures distributes the pressures P1, P2 in the supply lines 33, 34. According to the use (engine, pump, forward movement, backward movement), each line 33, 34 can bring or recover the oil, at high or low pressure.
The device 10 is typically housed in a case 23 of the machine 20, with the case comprising a first outlet 101, a second outlet 103, a first inlet 102, a second inlet 104 (see
Note that the device 10 functions in a similar manner with a single inlet and outlet instead of two inlets and outlets 101, 102, 103, 104.
The device 10 for controlling the displacement of a machine 20 with axial pistons therefore comprises the case 23 that houses a control unit S1 comprising:
These different elements are arranged in the following way:
More precisely, the control spool 110 has two ends 110a, 110b. The control spool 110 comprises at least one circular groove 111, 112, and preferably as mentioned hereinabove a first groove 111 that connects the first inlet 102 to the first outlet 101 and a second groove 112 that connects the second inlet 104 to the second outlet 103.
The second spool 130 comprises a head 131 and a body 132, with the head sliding in a plug 120 located on the axis of sliding Δ.
The axial force of the control pressure Ps is exerted via oil by a control pressure line 105 in a cavity formed by the case 23 and the first end of the piston 110a. The spring 140 exerts its force on the body 132 of the second tool 130 and on the second end of the control spool 110. This control pressure line 105 is typically of an on/off mode, that is to say that it is alternatively applied a pressure Ps or no pressure.
The control pressure line 105 can comprise a restriction, more preferably an orifice of 0.5 mm in diameter.
The axial force of the switching pressure Pm is exerted via oil by a switching pressure line 121 in a cavity 122 formed by said plug 120 and the head 131 of the second tool 130. The switching pressure line 121 is located in said plug 120.
In the case where there are two inlets and outlets 101, 102, 103, 104, the first supply line 33 is tapped by a first sampling 33a in order to supply the first inlet 102 and the second supply line 34 is tapped by a second sampling 34a in order to supply the second inlet 104.
The case 23 guides the control spool 110. The first end 110a of the control spool 110 and the case 23 form a cavity 113, of variable size according to the position of the control spool 110. The displacement pressure line 105 supplies said cavity 113 with oil under control pressure Ps. Preferably, when automatic mode is activated, the control pressure Ps is constant. In addition, it is typically comprised between 20 and 40 bars. In this way, the device 10 is such that the oil under pressure exerts a displacement force Fd on the control spool 110 according to the axis of sliding Δ, in the direction of the second tool 130.
Alternatively, the pressure Ps can be adjusted by the user in order to configure the operation of the machine.
As mentioned hereinabove, the communication between the inlets 102, 104 and outlets 101, 103 respectively is carried out by the two circular grooves 111, 112 (see
The second spool 130 slides in the plug 120 according to the axis of sliding Δ, which means that the displacements of the control spool 110 and of the second tool 130 are collinear. The plug 120 thus guides the second spool 130. The head 131 and the plug 120 form a cavity 122, of variable size according to the position of the second tool 130. The switching pressure line 121 supplies said cavity 122 with oil under switching pressure Pm. The switching pressure Pm typically corresponds to one of the supply pressures P1, P2 of the machine 20. It is therefore variable according to the load of the machine 20. It is typically between 40 and 250 bars.
In this way, the device 10 is such that the oil under switching pressure Pm in the cavity 122 exerts a counteracting force Fc on the head 131 of the second tool 130 according to the axis of sliding Δ, in the direction of the control spool 110.
The spring 140, as mentioned hereinabove, is located between the second end 110b of the control spool 110 and the body 132 of the second tool 130. Through the architecture of the device 10, the spring 140 exerts thrust forces (it is constantly in compression).
The spring 140 is in an oil bath. For this, a drainage circuit 150 makes it possible to supply the zone of the spring 140 with oil.
According to a preferred embodiment, the second end 110b of the control spool 110 comprises a recess 114 in which the spring 140 is partially housed (see
The drainage circuit 150 opens into the recess 114.
Except therefore in abutment, the second end 110b of the control spool 110 is therefore not in direct contact with the second tool 130.
Alternatively (not shown in the figures), the second end 110b of the control spool 110 cannot come into contact with the body 132 of the second tool 130: either the spring having a stiffness such that the displacement force Fd and the counteracting force Fc cannot compress it enough, or because its volume of material prevents the contact when it is fully compressed.
The displacement force Fd is equal to the product of the control pressure Ps of the oil in the displacement pressure line 105 with the area St of the section whereon the control pressure Ps is exerted, i.e. typically the section of the first end 110a of the spool 110: Fd=Ps×St.
Similarly, the counteracting force Fc is equal to the product of the switching pressure Pm of the oil in the switching pressure line 121 with the area Sp of the section whereon the control pressure Ps is exerted, i.e. the section of the head 131 of second spool 130: Fc=Pm×Sp.
By the arrangement of the elements described hereinabove, recall that the displacement force Fd and the counteracting force Fc are therefore exerted in the opposite direction.
The spring 140, as for it, opposes the displacements of the control spool 110 and of the second tool 130. Considering a fixed second spool 130 immobile, the spring therefore exerts its opposition force Fo (said force being equal to the product of its stiffness and of its difference in length with its length when empty) in the direction opposite that of the displacement force Fd. Considering a fixed control spool 110, the spring 140 therefore exerts its opposition force Fo in the direction contrary to that of the counteracting force Fc.
For all practical purposes, recall that the opposition force of the spring Fo on a part depends on the position of the part located on the other side, since this position has an influence on the length of the compressed spring 140.
The stiffness of the spring 140 and/or the control pressure Ps is chosen (according to the active surface of the mobile part) in such a way that the value of the minimum opposition force Fo is less than the displacement force Fd.
When the second spool 130 is in abutment in the plug 120, i.e. that the cavity 122 of the plug 120 is of minimum size, and that the displacement pressure line 105 does not supply the cavity 113 with oil under control pressure Ps, the spring 140 maintains the control spool 110 in idle position (i.e. the cavity 113 of the case 23 is of minimum size).
More generally, regardless of the positions of the control spool 110 and of the second tool 130, as long as the displacement force Fd is less than the opposition force Fo, the control spool 110 is maintained in idle position by the spring 140, as shown in
Note that if the cavity 122 of the plug 120 is at switching pressure Pm, the control spool 110 is a fortiori maintained in this idle position, as can be seen in
On the other hand, when the cavity 113 is supplied with oil under control pressure Ps, the control spool 110 can be put in the two positions without the length of the spring 140 changing. For this, the control pressure Ps must be able to generate a displacement force Fd that is higher than the maximum opposition force Fo, which is that obtained when the cavity 122 has a maximum volume, which is that of the spring that is the most strongly compressed.
Two cases are obtained:
More precise details on the state of the spring 140 in these cases shall now be provided.
According to a first embodiment (preferred) of the spring 140 and of the second end 110b of the control spool 110: with the control spool 110 assumed to be in working position, i.e. Fd>Fo, Fc is then applied on the second spool, with Fc>Fo. In this case, the spring 140 will be compressed until the body 132 of the second tool 130 is in contact with the second end 110b of the control spool 110. This is then two solid parts in contact, and the displacement is made in one direction or the other according to the value of the forces: the characteristics of the different elements (the control pressure Ps, the stiffness of the spring 140, choice of surfaces, etc.) are chosen during design in such a way that Fc can be greater than Fd, in this way the control spool 110 passes into idle position. Inversely, the spool 110 passes back into working position, when the switching pressure Pm decreases and satisfies Fc<Fd. The decrease in the switching pressure Pm is linked to the load of the machine 20 (increasing, decreasing, intense use, etc.).
According to another embodiment of the spring 140: the control spool 110 is assumed to be in working position, i.e. Fd>Fo, Fc is then applied on the second spool, with Fc>Fo. In this case, the spring 140 will be compressed until Fo=Fc (or reach its mechanical limit, i.e. its maximum physical compression, and in this case the spring behaves like a solid part and we also have Fo=Fc). The characteristics of the different elements (the control pressure Ps, stiffness of the spring 140, choice of surfaces etc.) are chosen during the design in such a way that Fc (then equal to Fo) can be higher than Fd, in this way, on a Fc=Fo>Fd, and therefore the control spool 110 passes to idle position. Inversely, the spool 110 passes back into working position when the switching pressure Pm decreases and satisfies Fc=Fo<Fd.
In the two cases consequently, when automatic mode is activated (i.e. the line 105 is brought to the pressure Ps, which enables activating Fd that opposes to Fc), the controlling of the control spool 110 is controlled by the algebraic value Fd-Fc, and the value of the force Fo of the spring 130 no longer intervenes, contrary to prior art of Kayaba described in the introduction.
More concretely, the adding of a second spool 120 means that the spring exerts its force of each side on a different spool that each one is mobile and displaced by the oil pressure. Consequently, the two opposing forces exerted by the spring offset each other.
In the same compact and structurally close device solutions without automatic mode, a device is obtained with non-automatic mode which takes full advantage of the spring in order to maintain the device 10 in idle position and an automatic mode which makes it possible to overcome the spring in order to switch between the idle position and the working position according to solely the control Ps and switching Pm pressures.
In relation with the hydraulic circuit 30, when the device 10 is in working position, the first sampling 33a is connected to the first cylinder line 31 via the first inlet 102, the groove 111 and the high pressure outlet 101, in order to allow for the activation of the cylinder 31a. In the idle position, the cylinder lines 31, 32 are no longer supplied with oil under pressure. In this position, cylinder lines 31, 32 are both connected to an emptying line.
In idle position, respectively working position, the machine 20 is said to have a large displacement, respectively small displacement.
When the auto shift mode is activated (i.e. the line 105 is brought to the pressure Ps):
Two embodiments of the unit S1 are now given.
In a first embodiment (
The distributor 40 integrates non-return valves 41 in the direction of the supply lines 33, 34 of the machine 20.
In this embodiment, the circuit 30 can comprise at least two pressure limiters 36 between the two supply lines 33, 34, in two different directions.
In a second embodiment (
Three of the positions are similar in function to the preceding distributor 40.
Except for the switching line 121, document EP 2 592 263 describes one this unit S1.
In the two additional positions:
By comparing the architecture of the device 10 in relation to the solution of prior art without automatic mode (
Finally, with regards to the case 23 of the machine 20, the latter simple requires a modification in the vicinity of the plug 120 and of the second spool 130.
| Number | Date | Country | Kind |
|---|---|---|---|
| 1463288 | Dec 2014 | FR | national |
