JPS6330676A - Solenoid operating fluid pressure adjusting valve - Google Patents

Abstract

(57) [Abstract] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a fluid valve assembly, for example as specified in the preamble of claim 1, as disclosed in US-A-3,688,607.

As is commonly known in the art, solenoid-operated valves, such as those used in automatic transmission control systems, are fully compatible with microprocessors, but typically have high hysteresis and very low temperatures. invalid control of
There is a problem of nonlinearity. Furthermore, such throttle-actuated valves are generally sensitive to supply pressure changes, exhibit low flow capacity, pulsate control pressure, exhibit substantial power demands, and degrade as duty is extended. Such pressure control valves typically include valve element(s)
depends on the dwell time at each extreme of travel of the valve, operates independently of any pressure feedback, and/or is force dependent on the particular valve element position forced by the solenoid.

The present invention seeks to provide a relatively simple solution to these problems.

To this end, the fluid valve assembly according to the invention has the features specified in the characterizing part of claim 1.

Thus, the fluid valve assembly of the present invention achieves the desired results by combining a linear solenoid with an asymmetric spool valve.

The fluid valve assembly of the present invention has the potential to utilize a combination of linear solenoids and asymmetric spools to provide fluid pressure regulation and circuit sequencing.

Linear solenoids, also known as proportional solenoids, shunt magnetic field lines with core motion to provide a core output on the valve that is a function of coil current independent of core position.

In one particular embodiment of a fluid valve assembly according to the present invention, in the form of a pressure-actuated fluid pressure regulating valve,
The spool valve connects the exhaust and supply [] to the regulated pressure [
1 and to provide a regulated pressure area on the spool valve in its force equilibrium and thereby to provide an area of imbalance acted upon by the regulated pressure to produce an internal pressure return. have unequally spaced areas of diameter. During regulation, the asymmetric spool valve thus operates as an internal pressure return pressure regulator;
The linear solenoid operates as a current-carrying transducer, which is independent of the core and thus of the valve position over its operating range.

This interaction between the current dependence/position independence of the force output of a linear solenoid and the pressure feedback of an asymmetric spool valve makes the dictation a function of the relative levels of force generated by the solenoid and spool valve, and for high pressures is taken as a function of the opposing spring force. A controlled or regulated pressure is the result of a balance of these forces, so that the effect of varying the supply pressure is substantially reduced or provided with a relatively high flow capacity or minimal pulsations of the controlled pressure.

Furthermore, low power is required and flow rate is substantially unaffected by duty cycle.

Moreover, the supply port can be eliminated, and the device can then be used as an electrically variable 20 pressure relief valve with high flow capacity allowing supply pressure adjustment.

In addition, such biro arrangements can also be plumbed to provide electrically adjustable sequencing of fluid circuits.

Referring now to the drawings, FIG. 1 shows a linearly variable, typically high control pressure in control line 16 to actuate, for example, a converter clutch slip controller (not shown) in supply line 12 and exhaust line 12. A fluid pressure actuated solenoid, generally indicated at 10, adapted to operate with oil as the working medium in the transmission control system to connect line 14 to the control line alternatively. A fluid valve assembly in the form of a regulator valve is shown.

Valve assembly 10 generally includes supply and exhaust lines 12 and 1.
4 and a control line 16.

Within the spool valve portion of the valve assembly, conduit 12 is connected as shown.
, 14 and 16 are open holes 2 in the manifold 26.
A cylindrical valve housing 22 is received within 4. The valve housing 22 has an axle opening on its exterior to the respective conduits 12.14 and 16 in the manifold bore 24 and communicating them with the interior of the valve housing via diametrically opposed ports 34.36 and 38, respectively. annular grooves 28, 30 and 32 spaced apart in the direction. The latter includes a large diameter region 44 and a small diameter region 4 formed on the spool valve 18.
A service hole 39 is formed having a large diameter section 40 and a small diameter section 42 respectively receiving 6, these components being oriented such that the large diameter region controls the exhaust port and the small diameter region controls the supply port 1. There is.

The valve regions 44 and 46 are controlled by - a first control (regulated) pressure port 38 remaining open to the space between the regions throughout the movement of the spool valve 18 between the supply and exhaust positions; In the feeding position shown in the figure, the small diameter @@46
The supply pressure [ ] 34 is released and the large diameter region 44 is connected to the exhaust port 3.
6 to the control pressure port 38, and in the exhaust position, simultaneously with the upward movement of the valve, the large diameter region opens the exhaust L1 and the small diameter region closes the supply port to the control pressure [1, the latter axially spaced to provide fluid supply or exhaust to the mouth of the valve.

Additionally, although the supply, exhaust, and control ports are preferably formed in pairs as shown, they may be formed as a single port, or depending on various design and/or manufacturing considerations. It may be formed by dividing into a larger number of parts. However, in any case, the spool valve is basically 3
0 configuration, ie one with one inlet, one outlet and one control [ ].

The linear solenoid 20 of the solenoid actuated fluid pressure 31 valve assembly 10 consists of a bobbin assembly 50 formed of two flanged end pieces 52 and 54 joined by a sleeve 56.

A coil (winding) 58 is wound around the bobbin assembly and is enclosed by a cylindrical a-wall 60. The bobbin end piece 54 and thus the solenoid is connected to the valve housing 22 by a threaded fitting 61. A bushing 62 is fixedly mounted in a hole 64 passing through the bobbin end piece 54, which is connected to the spool valve 18 at the upper end 14i68 and secured to the core 72 by a threaded connector 70 at the lower end. A plunger to be formed is slidably received therein.

The core 72 is movable within the bobbin sleeve 56 together with the shaft 66 and is received at its upper end in a correspondingly shaped internal conical portion 76 of the bobbin end piece 54 to reduce air gaps and simultaneously with the upward movement of the core. It has an outer cone 74 that diverts the flow away from the location shown to provide the desired linearity between current and core displacement.

A plug 78 is threaded into the upper end of the valve housing 22, and a coil return spring 80 received between the plug 78 and the upper end of the spool valve acts to press the latter downwardly against the solenoid shaft 66. , its downward motion is 1i! 1h66
The fully retracted position shown is restricted by a retaining ring 82 which is retained within the annular groove and engages the upper end of the bushing 62.

The coil return spring 80 normally biases the spool valve to this fully retracted (supply) position shown, but in this position the exhaust port 36 is closed by the large diameter region 44 of the spool valve and the control pressure port 38 is not supplied. [It opens past the small diameter region 46 with respect to 134.]

Solenoid coil 58 is connected to DC power source 84 by a controller 86 of known design incorporating a pulse width modulated drive circuit and programmed to provide the desired valve function.

With no current applied to the controller or coil 58, the spring 80 is adjusted to provide a preload to overcome only the spool differential force and to provide the desired maximum control pressure (usually the supply pressure). This spool operating force is a force generated by the il+ control pressure acting between regions 44 and 46 in the unbalanced region -H of the large diameter region.

The spool valve regions 44 and 46 form an open variable flow area passageway therebetween such that when the pressure in the control port increases above a desired level, the spool differential force and additional solenoid force (moves and overcomes the spring force). The spool valve is moved in a direction that brings the control port into communication with the exhaust port.Alternatively, if the pressure in the control port drops below the desired pressure, the spring force overcomes the combined force of the differential spool valve and the additional solenoid force. The control pressure is increased by moving the spool valve in a direction that brings the control [1] into communication with the supply port.

When the control pressure is at the desired pressure level, the face blades are balanced and the spool valve is in a position that does not communicate the control port with either the supply port or the exhaust port.

Because the In pressure is the result of a double-edged equilibrium that includes the solenoid's force, and because the solenoid's output is proportional to the current supplied to it and independent of the spool valve position, supplying and varying the current to the solenoid The operation of the controller for this purpose precisely adjusts the control pressure linearly to the desired control pressure level, thereby decreasing the control pressure from the maximum value at the lowest current in proportion to the increasing current supply (Figures 4 and 4). (see curve 88 in Figure 5).

Additionally, since the solenoid current is controlled by a pulse width modulation drive circuit and the pulse nature of the current affects the amplitude of movement of the solenoid core and thus the spool valve, the amplitude is controlled by the pulse width modulation frequency, reducing hysteresis. It acts to lower the The result is a highly desirable linear force vs. valve stroke characteristic, as depicted in FIG. Even at operating temperatures as high as 100°C, there is virtually no hysteresis, as shown by closed-loop curve 90 in the figure (the graphs in Figures 4 and 5 plot the control pressure against the current to the solenoid coil) .

Traditional time-modulated, solenoid-operated valve systems
High force levels with short time constants are typically required to minimize and stabilize valve member position transition times. To achieve high force levels with short time constants, these devices typically require relatively high power, low inductive reactance solenoids. The fluid valve assembly of the present invention does not rely on time modulation and therefore requires inherently less power.

Moreover, valve member transition time is not a critical consideration in the fluid valve assembly of the present invention, so longer, larger area ports can be used to increase flow to very high flow rates.

For applications where control pressures are typically low, a low pressure version of the pressure regulating valve comprising the fluid valve assembly of the present invention is provided, as shown in FIG. Note that in FIG. 1, reference numerals that are the same as in FIG. 1 but with a ' (such as N') designate structures and related parts similar to those in FIG.

Specifically, typically in low pressure versions, the valve assembly 10' is inverted relative to the solenoid 20', and the larger diameter spring 80' projects radially outwardly thereof, formed at F. The annular seat 102 is located around the plunger 66' between the annular seat 100 and the annular seat 102. The annular seat 102 is located on the plunger edge 54' in the space previously occupied by the lower end of the plunger bush 62'. It is full of formations,
Therefore, the plunger bush 62' is shortened and the hole 64' is shortened.
remains fixed within.

With this arrangement, fluid pressure from the differential spool region acts on the linear solenoid to balance the forces and control the pressure at control port 38'. for example,
When there is no solenoid current, the spool differential force is applied to valve 18.
' is moved downwardly to communicate with the control port 38' and the exhaust port 36' to provide a minimum pressure at the true mouth.

Control pressure changes are made in a manner similar to the conventional high pressure system shown in FIG. 1, except for the inverted arrangement of the supply and exhaust ports and the spool valve asymmetry.

As a result, the solenoid current, which remains proportional to the output, is generally inversely proportional to the desired control pressure.

The return spring 80' has a substantially lower spring rate than the corresponding spring 80 in FIG. Configured with a load. In this version, the spring 80' does not exert a significant force in balancing the valve force to control the pressure and may be omitted if reliability of opening of the outlet is not an important requirement. good.

Similar to the high pressure system shown in FIG. 1, the low pressure system shown in FIG. It has also been found that low pressure applications exhibit virtually no bisteresis, even at fluid operating temperatures as high as 100 DEG C., as shown by closed loop curve 90' in FIG.

Some fluid power systems, such as those with pumps, deliver a specific output pressure that is inversely proportional to the output flow. While the pressure and flow levels may change during continuous delivery operating conditions, this overall inverse relationship remains. In these systems, line pressure is a function of total output flow and feed conditions (eg, pump speed and fluid temperature).

A further variation of the solenoid operated fluid valve assembly in the form of a solenoid operated fluid pressure regulating valve according to the present invention operates to regulate the overall system output flow to regulate the system supply line pressure. Yes, and is shown in FIG. 6 as typically configured for high pressure applications.

In this model, it is the same as in Fig. 1, but with `` (N
'') are used to indicate a structure similar to that of FIG. Pressure acts on the unbalanced region of the spool valve 18'', acting in conjunction with the controllable force of the solenoid 20'' to exert a force counteracting the force of the return spring 80''.
0 configuration is obtained. When the supply pressure increases above a predetermined level, both the fluid and solenoid forces overcome the return spring force and the spool valve 18'' moves to increase the open flow area of the exhaust port 36'', thus reducing the overall system flow. This reduces the supply system pressure. If the system pressure is below a predetermined level, for example due to increased flow or lower pump speed elsewhere in the system,
The fluid force acting on the spool valve is lower, and the return spring forces the spool valve to move to reduce the open exhaust flow area at the exhaust port 36'', thus reducing flow and thereby increasing system pressure.

Additionally, the Model 20, which provides flow proportional to system supply pressure, allows fast response/variable offsets to be applied through linear solenoid action. These control operations combined with fluid supply characteristics 4) J quality are as follows.
C variable pressure/flow equilibrium points can be achieved. Additionally, Type 20 of the solenoid-operated pressure regulating valve has a second
Similar to the 30 low pressure version shown in the figure, it can be constructed in either a normal low pressure configuration or a normal high pressure configuration as shown in FIG.

Many fluid power circuits are configured to cause a sequence of separate actuations to occur based on increased pressure within a single control line. Automatic adaptive planning is almost impossible to implement because adjustments to the time between phases are typically required, and this is extremely difficult to achieve in such devices after initial calibration. That's why.

20 of the solenoid operated pressure regulating valve shown in FIG.
The model provides an easily variable fluid sequencing device to meet such requirements. In this model, the same reference numerals as in Fig. 1 but with a ' (such as N'') are used to indicate a structure similar to that in Fig. 1, and similar to the type 20 in Fig. 6. Although the control port located in the middle is omitted, in this example, the remaining ports 34'' and 36''
``'' are connected to the primary and secondary circuits via lines 12' and 14'', respectively.

The primary circuit port 34'' is connected to the I-controlled device (
The rising pressure signal applied to the spool valve 18'' (not shown)
′ is also allowed to be applied so as to act on the differential region of ′. As before, the fluid force generated by this is applied to the return spring 8
It acts with a variable force of the linear solenoid 20'' against the 0'' force.

Communication between ports 34'' and 36'' is prevented until the primary circuit pressure at the former [1] rises to a predetermined level established by opposing solenoid and spring forces. However, when such a level is reached, the spool valve 18'' moves to open the secondary [136'''', thus conduit 12''
As a result of the connection of the line 14'' and the line 14'', pressure is allowed to rise in the secondary circuit.

The apparatus of FIG. 7 thus provides rapidly variable control for sequencing two fluid lines (circuits). Furthermore, the device communicates with the primary circuit, which increases the pressure of the secondary circuit until the primary circuit reaches a predetermined pressure level, and beyond this level, the device allows both circuits to operate independently. It can also be configured as a normally open type that prevents connection.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view of one embodiment of a fluid valve assembly according to the present invention adapted to establish clutch control pressure in an automotive automatic transmission control system as a solenoid actuated fluid pressure 3I regulator; 2 is a longitudinal sectional view similar to FIG. 1, but of a 30 normally low pressure version of a fluid valve assembly according to the invention adapted as a solenoid operated fluid pressure regulating valve; FIG. Graphs explaining the Kerr process PL of the solenoid-operated fluid pressure regulating valve shown in the figure. Graph illustrating hysteresis characteristics with fluid temperature; FIG. 6 is a longitudinal cross-sectional view of a type 20 solenoid operated fluid valve assembly according to the invention similar to FIG. 1 but adapted as a fluid pressure regulating valve; FIG. 2 is a longitudinal cross-sectional view of another embodiment of a Type 20 solenoid operated fluid valve assembly of the present invention similar to FIG. 1 but adapted as a fluid pressure regulating valve; FIG. [Explanation of symbols of main parts] 10... Fluid pressure regulating valve 12... Supply port 14... Exhaust port 16... Control port 18... Spool valve 20... Solenoid 44... Suburf ? Large diameter region 46 of spool valve - Small diameter region 72 of spool valve Core 80 Coil return spring ii

Claims (1)

[Claims] 1. A solenoid (72) acts on a spool valve (18) having spaced areas (44, 46) of unequal diameter to provide controlled communication between at least two ports (12, 14, 16). In the fluid valve assembly included in the solenoid (20), the solenoid (20) is connected to the solenoid (20).
said diameter of the spool valve (18), having a fluid path on the core (72) that provides an output on the core (72) that is proportional to the current supplied to the spool valve (18) and independent of the core position within a finite range of displacement. The unequal areas (44, 46) form a variable area flow path between the ports (12, 14, 16) and impose a controlled fluid force on the spool valve (18) thereby , 14, 16) characterized in that it also has a region of fluid pressure imbalance exerted by the fluid pressure at one (16) of the ports (12, 14, 16) to ultimately control the communication between the mouths (12, 14, 16). Fluid valve assembly. 2. In claim 1, the controlled fluid force is applied to a spool valve (1) in a direction opposing the solenoid output.
8) A fluid valve assembly, characterized in that it is pressed onto the fluid valve assembly. 3. In claim 1, a spool valve (1
8) has a spring means (80
) and the controlled fluid force exerted on the spool valve (18) acts in the same direction as the solenoid output. 4. In any one of claims 1 to 3, the fluid valve is a fluid pressure regulating valve (10), and the mouth (12, 14, 16) of the spool valve (18) is the supply port (12). , exhaust port (1
4) and a control port (16), the spool valve (18) selectively communicates the supply port (12) and the exhaust port (14) with the control port (16). fluid, characterized in that the imbalance area of the spool valve (18) is acted upon by the regulated pressure to bring about a regulated fluid pressure on the spool valve (18). valve assembly. 5. In claim 4, the spool valve (1
8) The regulated pressure in the areas (44, 4) of the spool valve (18) is such that the regulated fluid pressure on the spool valve (18) is effective in balancing the spool valve (18) in such pressure regulation.
6) A fluid valve assembly characterized in that it acts on an area of imbalance between.