HYDRAULIC CONTROL DEVICE AND MARINE TRANSMISSION

Abstract

A hydraulic control device with a pressure control valve that has a control piston and a modulating piston which can move relative to one another. The control piston and the modulating piston are pushed apart from one another by at least one spring. At one end face of the modulating piston there is arranged a pressure chamber in such a manner that when the pressure chamber is filled, the modulating piston is caused to move in the direction toward the control piston. The pressure chamber can be filled by a first volume flow Q1 of a pressure medium. A venting line, with at least one further throttle, is connected to the pressure chamber. A second volume flow Q2 can be discharged, via the venting line, from the pressure chamber, The hydraulic control device can be utilized in a marine transmission,

Claims

1-6. (canceled)

7. A hydraulic control device (20) with a pressure control valve (1), the pressure control valve (1) comprising: a control piston (3) and a modulating piston (4) being are movable relative to one another, the control piston (3) and the modulating piston (4) being pushed apart from one another by at least one spring (7), a pressure chamber (8) being arranged, at one end face of the modulating piston (4), in such a manner that when the pressure chamber is filled, the modulating piston (4) being moved in a direction toward the control piston (3), the pressure chamber (8) being fillable with a first volume flow (01) of a pressure medium through a first throttle (9), and a venting line (21) with at least one further throttle (22), through which a second volume flow (Q2) can be discharged from the pressure chamber (8), being connected to the pressure chamber (8).

8. The hydraulic control device according to claim 7, wherein respective dimensions of the first throttle (9) and the further throttle (22) are matched to one another in such a manner that a third volume flow (Q3), which is a difference between the first volume flow (Q1) and the second volume flow (Q2), is produced in the pressure chamber (8), and this differential volume flow behaves in a temperature-stable manner or has a desired temperature dependence.

9. The hydraulic control device according to claim 7, wherein at least one of the first throttle (9) and the further throttle (22) is designed as temperature-dependent self-adjustable throttle(s), and the temperature-induced adjustment of each temperature-dependent self-adjustable throttle is selectively chosen such that a third volume flow (Q3), which is a difference between the first volume flow (Q1) and the second volume flow (Q2) and which behaves in a temperature-stable manner or with a desired temperature-dependence, is produced in the pressure chamber (8).

10. The hydraulic control device according to claim 7, wherein the venting line (21) opens into a spring chamber (12) of the pressure control valve (1) in which the at least one spring (7) is arranged.

11. The hydraulic control device according to claim 7, wherein the venting line (21) is integrated together with the further throttle (22) in the modulating piston (4).

12. A marine transmission with a hydraulic control device (20) according to claim 7.

13. A hydraulic control device with a pressure control valve comprising: a control piston and a modulating piston being coaxially movable relative to one another, at least one spring being arranged between the control piston and the modulating piston and axially pushing the control piston and the modulating piston in opposite directions away from one another, a pressure chamber being arranged adjacent an end face of the modulating piston such that pressurization of the pressure chamber, by a third volume flow of pressure medium, pushing the modulating piston in a direction toward the control piston, a first volume flow of the pressure medium flowing, via a first throttle, into the pressure chamber for pressurizing the pressure chamber, a venting line being connected to the pressure chamber and having a second throttle through which a second volume flow of the pressure medium can be discharged from the pressure chamber, and the third volume flow being equal to a difference between the first volume flow and the second volume flow.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Further features and advantages of the invention emerge from the attached figures and the figure description given below.

[0019] The figures show:

[0020] FIG. 1: A section of a hydraulic control device for a marine transmission according to the prior art, represented schematically;

[0021] FIG. 2: A diagram showing the pressure variation of a clutch pressure in a marine transmission having a hydraulic control device according to FIG. 1;

[0022] FIG. 3: A section of a hydraulic control device according to the invention for a marine transmission, represented schematically; and

[0023] FIG. 4: A diagram showing the pressure variation of a dutch pressure in a marine transmission having a hydraulic control device according to FIG. 3.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0024] The principle of the structure of part of a hydraulic control device with a pressure control valve 1 according to the prior art is shown in FIG. 1. The pressure control valve 1 comprises a control piston 3 and a modulating piston 4, which are arranged coaxially with one another in a control housing 2 and which can move relative to one another. The control piston 3 and the modulating piston 4 are arranged and can move in respective bores 5, 6 of the control housing 2. The bore 5 of the control piston 3 is arranged coaxially with the bore 6 of the modulating piston 4 so that the control piston 3 is also arranged coaxially with the modulating piston 4. The bore 5 of the control piston 3 has a smaller diameter than the bore 6 of the modulating piston 4. Correspondingly the diameters of the two pistons 3, 4 are also different, Between the control piston 3 and the modulating piston 4 there is arranged a spring 7, which pushes the two pistons 3, 4 apart from one another. In this case, the spring 7 is in the form of a spiral compression spring, At one end face of the modulating piston 4 a pressure chamber 8 is arranged in such manner that when filled, it pushes the modulating piston 4 in the direction toward the control piston 3.

[0025] The pressure control valve 1 has an oil supply connection 13 which is connected to a pump (not shown). The pump supplies the pressure medium to the oil supply connection 13 at a sufficient system pressure. In addition the pressure control valve 1 has a lubrication connection 14, by way of which various lubrication points can be supplied with pressure medium, The pressure medium can serve at the same time for the lubrication and the cooling of components.

[0026] Finally, the hydraulic control device comprises a clutch valve 16, which is arranged in a clutch pressure line 15. By actuating the clutch valve 16, a pressure outlet of the pressure control valve 1 can be connected via a clutch pressure connection 17 to a pressure chamber of a hydraulically actuated shifting clutch 19, When the clutch valve 16 is not actuated, the associated shifting clutch 19 is or will be vented. The modulating piston 4 is then on the right in FIG. 1 against the stop. The spring 7 pushes against the control piston 3 and correspondingly a lower pressure is produced in accordance with the spring force of the spring 7, which is present at the dutch valve 16. If now the clutch valve 16 is actuated, then the pressure medium flows into the pressure chamber of the shifting clutch 19 but also, via a connection line 18 and a first throttle 9 into the pressure chamber 8 behind the modulating piston 4. In that way the pressure chamber 8 can be filled with pressure medium via the first throttle 9, A non-return valve 11, which is arranged in the connection line 18 parallel to the first throttle 9, is closed during the filling of the pressure chamber 8. The volume flow passing through the first throttle 9 into the pressure chamber 8 during the filling of the pressure chamber 8 is called the volume flow Q1.

[0027] In FIG. 1 a first pressure p.sub.1 is plotted, which is present between the clutch pressure line 15 and the first throttle 9. In addition, in FIG. 1 a second pressure p.sub.2 is plotted, which is present in the connection line 18 between the first throttle 9 and the pressure chamber 8. In this case the following relationships apply, at least approximately:

p.sub.1=F_pressure spring/A_control piston;

and for p.sub.2, at least approximately,

p.sub.2=F_pressure spring/A_modulating piston,

where [0028] F_pressure spring is the spring force of the spring 7, [0029] A_control piston is the area of the control piston and [0030] A_modulating piston is the area of the modulating piston.

[0031] Since A_control piston is smaller than A_modulating piston, at the first throttle 9 there is correspondingly a positive pressure difference or pressure drop, which brings about the volume flow Q1. Here, the first throttle 9 is the sum of the flow resistances of lines, an aperture if there is one and a filter sieve.

[0032] The pressure chamber 8 is now filled when the clutch valve 16 is actuated, and the modulating piston 4 correspondingly moves slowly to the left and further prestresses the spring 7. A pressure ramp is produced. In this variant, the pressure ramp rises until the modulating piston 4 finally contacts the control piston 3, which is then necessarily pushed to the left and closes the control edge for lubrication 14. The pressure then increases abruptly to a system pressure level which is regulated by a system pressure valve (not shown). The control piston 3 has a control geometry with control edges which, when the control piston is moved, controls the pressure at the clutch pressure connection 17 and thus also the pressure p.sub.1. The function of the pressure control valve 1 now ensures that the pressure p.sub.1 increases, whereby the pressure in the pressure chamber of the associated shifting clutch 19 increases correspondingly. This function of the pressure control valve 1 is familiar to a person with knowledge of the field, for example from EP 1 980 767 A2 which was mentioned earlier, to which reference is made at this point.

[0033] The flow resistance of the first throttle 9 acting on the volume flow Q1 is a function of the viscosity of the pressure medium. Thus, the volume flow Q1 varies as a function of the temperature of the pressure medium. Accordingly, the speed of the modulating piston also changes with temperature. Thus, in this varient the shifting time of the hydraulically actuated shifting clutch 19 is subject to considerable temperature-dependent fluctuations.

[0034] The temperature-dependent fluctuations can be seen in FIG. 2. FIG. 2 shows a diagram with the pressure variation of a clutch pressure when the shifting clutch 19 is actuated, in the case of a conventional hydraulic control device 10 in cold and hot conditions.

[0035] The time t is shown along the horizontal axis of the diagram. The vertical axis represents the clutch pressure p. The solid functional line represents the variation of the clutch pressure when the shifting clutch 19 is engaged in hot conditions, for example at 80 degrees Celsius. The dotted line represents the variation of the clutch pressure when the shifting clutch 19 is engaged in cold conditions, for example at 10 degrees Celsius. It can be seen clearly that under cold conditions the clutch pressure increases after a substantial time delay. The result of this is that the shifting clutch is closed with a corresponding time delay. Such temperature-induced variations of the shifting times of the shifting clutch are undesirable.

[0036] The remedy for the problematic temperature-dependent shifting times is shown in FIG. 3 in the form of the hydraulic control device 20 according to the invention for a marine transmission, The hydraulic control device according to FIG. 3 corresponds to a very large extent with the control device according to FIG. 1, Accordingly, the same components in FIGS. 1 and 3 are given the same indexes and equivalent functions will not be explained again here.

[0037] In the hydraulic control device 20 according to the invention a venting line 21 with a further throttle 22 is connected to the pressure chamber 8, Via the venting line 21 with the further throttle 22, a second volume flow Q2 can be discharged from the pressure chamber 8, so that in the pressure chamber 8 a volume flow Q3 is obtained as the difference between the first volume flow Q1 and the second volume flow Q2. The dimensions of the first throttle 9 and the further throttle 22 are matched to one another in such manner that the volume flow Q3 remains at least approximately constant with temperature. In that way the modulated pressure build-up after the clutch valve 16 has been actuated always takes place in the same way regardless of the temperature. Consequently, the shifting times of the shifting clutch 19 are also independent of the temperature of the pressure medium.

[0038] In other words, an additional consumer in the form of the venting line 21 with the further throttle 22 is added to the pressure chamber 8. The pressure medium can be vented through the venting line 21, for example into a return container 23. From the return container 23 a pump can draw off the pressure medium again and circulate it, The further throttle 22 or the volume flow through the further throttle 22 is viscosity-dependent or temperature-dependent as well. However, the diameters and bore lengths of the two throttles 9 and 22 are now matched to one another in such manner that the volume flow Q3 in the pressure chamber 8 behaves in a temperature-stable manner. The following relationship applies:

Q3=Q1−Q2, whereby [0039] Q3 is the resulting volume flow in the pressure chamber 8, [0040] Q1 is the volume flow through the first throttle 9, and [0041] Q2 is the volume flow through the further throttle 22.

[0042] If the volume flow Q1 decreases due to increasing viscosity, then Q2 as well decreases and the result of the subtraction Q1−Q2 ideally remains constant. Thus, the influence of viscosity or temperature is substantially reduced or even eliminated. The pressure modulation and the shifting times are still only very slightly dependent on the pressure medium and its temperature.

[0043] A constant small amount of oil flows through the valve or through the piston chamber 8 behind the modulating valve. This has the advantage that over prolonged periods of inactivity air can escape, which due to its compressibility could otherwise have adverse effects on the pressure modulation and the shifting behavior, Furthermore residual oil is flushed out, which for example has still remained in the piston chamber after a transmission test run. Undesired temperature differences are also equalized by the continuously flowing amount of oil. A further advantage is obtained in that for the first throttle 9 larger diameters can be chosen without prolonging the shifting time. This reduces the risk that the throttles 9, 22 might become blocked. The ratio of diameter to bore length is improved by increasing the diameter and the first throttle 9 becomes very close to an ideal aperture, which in turn also has a positive effect on the temperature behavior. An ideal aperture is an abruptly occurring constriction in a rotationally symmetrical duct in the form of a bore with as short a bore length as possible, wherein the ratio of aperture diameter to duct diameter is smaller than 0.2.

[0044] A further advantage is the simple implementation of the invention. For example no additional components are needed if the further throttle 22 is integrated in the modulating piston 4 and vented into the spring chamber 12, For this, for example, a simple through-bore through the end face of the modulating piston 4 may be sufficient as the further throttle 22. In that case the through-bore connects the pressure chamber 8 to the spring chamber 12 and thus constitutes the venting line 21 with the further throttle 22. Preferably, the diameter of such a through-bore is matched to the dimensions of the first throttle 9 in such manner that the control device behaves in a temperature-stable manner, as explained above.

[0045] Finally, FIG. 4 shows a diagram with the pressure variation of a clutch pressure when the shifting clutch 19 is actuated, with the control device 20 according to the invention in cold and hot conditions.

[0046] Again, time t is plotted along the horizontal axis of the diagram while the vertical axis represents the clutch pressure p. The solid line shows the variation of the clutch pressure when the shifting clutch 19 is engaged in hot conditions, for example at 80 degrees Celsius. The dotted line shows the variation of the clutch pressure when the shifting clutch 19 is engaged in cold conditions, for example at 10 degrees Celsius. It can be seen that in cold conditions the clutch pressure increases with almost no time delay compared with the pressure increase under hot conditions. As a result, even in cold conditions the shifting clutch 19 is closed almost without any time delay. Slight delays, as shown by the slight deviation between the two function lines shown in FIG. 4, can also still occur in practice. However, by virtue of the invention such delays can be reduced at least to the extent that the delayed shifting times of the shifting clutch 19 are no longer perceptible to the master of the vessel.

[0047] It may even be that in certain applications or shifting clutches a slightly extended shifting time may be desired, since particularly in the case of large clutches the filling time when the oil is cold also lasts longer as a rule. By virtue of the present invention, however, a slightly longer temperature-dependent shifting time for that purpose can be selectively adjusted and does not occur randomly.

INDEXES

[0048] 1 Pressure control valve

[0049] 2 Control housing

[0050] 3 Control piston

[0051] 4 Modulating piston

[0052] 5 Bore

[0053] 6 Bore

[0054] 7 Spring

[0055] 8 Pressure chamber

[0056] 9 First throttle

[0057] 10 Hydraulic control device

[0058] 11 Non-return valve

[0059] 12 Spring chamber

[0060] 13 Oil supply connection

[0061] 14 Lubrication connection

[0062] 15 Clutch pressure line

[0063] 16 Clutch valve

[0064] 17 Clutch pressure connection

[0065] 18 Connection line

[0066] 19 Shifting clutch

[0067] 20 Hydraulic control device

[0068] 21 Venting line

[0069] 22 Further throttle

[0070] 23 Return container