JPS58188757A - Pressure fluid feeding device - Google Patents

Abstract

PURPOSE:To reduce the flow passage resistance and improve the reliability of an action by improving the feedback passage of a flow control valve which feeds back the excessive fluid to a tank side in said device which selectively feeds the pressure fluid discharged from multiple pumps to a fluid equipment. CONSTITUTION:When the feeding device is applied as a car power steering device 5, it is provided with a flow passage transfer mechanism 4 for selectively feeding the pressure oil discharged from the first and second pumps 1, 2 to the steering device 5. The transfer mechanism 4 is constituted with a flow passage transfer valve 12 which operates by detecting the pressure change of the pressure oil through a main passage 10 in response to the quantity of the load of the steering device 5 and a flow control valve 20 which releases a part of the flow flowing through the main passage 10 to a tank 3 side when the flow is a predetermined quantity or more. A valve hole 20a containing a spool 21 of the flow control valve 20 is provided with a feedback passage 28 made of a small diameter passage 28a and a nearly L-shaped hole 28b having a partially overlapped portion with the passage 28a.

Description

[Detailed description of the invention]

The present invention relates to a pressurized fluid supply device for selectively supplying pressurized fluid discharged from a pump to a fluid device.
l Concerning controlled pulp. For example, in a power steering device mounted on an automobile that eliminates the driver's steering effort, a pump that is a source of hydraulic pressure is usually rotationally driven by an automatic engine. and,
The amount of hydraulic fluid discharged from this pump increases or decreases in proportion to the engine's rotational speed. Therefore, such a pump is required to have a capacity capable of supplying a sufficient flow rate to the fluid W& device such as the power steering device even when the engine is in a low rotation range, that is, when the pump discharge ii is small. However, if the pump capacity is set in this way, an unnecessarily large flow rate will be supplied to the power steering device when the engine rotates at a high speed, resulting in a lot of waste, and the horsepower consumed by the engine for the pump will also be large. Unfavorable from an energy standpoint. %, in recent years there has been a call for improved fuel efficiency of automobile engines, and it is desired to minimize the horsepower consumption for the newly developed power #2 pump. For this purpose, two pumps with small capacities and a 61i' path switching valve are used, and when the discharge amount of each pump is small, these are combined and supplied, and when the discharge amount of each pump becomes large, one pump is used. In addition to supplying only the pressure oil from the tank to the power steering system, an externally powered pump is connected to the tank side to recirculate the pressure oil, minimizing the amount of horse power required to drive this pump. A pressure flow one-piece supply device that reduces the roasting force has been proposed in the past.
However, from A, the shark 1 mentioned above

['Blue, F, ν1 of the flow path based on the discharge amount of each pump, that is, the engine rotation speed
This configuration reduces energy loss when the car is running at high speeds, that is, when the engine is running at high speeds, but on the other hand, at low engine speeds (zero energy loss is unavoidable). However, there is still room for improvement.In the above-mentioned power steering system, pressure oil binding becomes a problem when high loads are applied and high outputs are applied.
At other times, such as when the vehicle is stopped or when the vehicle is over-driving, the supply of pressure oil is low even when the engine is in a low rotation range. good. In particular, cars often drive in urban areas using a 10-mode driving pattern, for example, up to 4 times.
It is necessary to reduce the horsepower consumption during such low-speed running. For this purpose, the flow path v/J#! which senses and operates when a negative ILF is applied to the power steering device is required. It would be good to adopt a mechanism, but the problem with a machine like this is that the engine rotates at high speed, and even if the discharge volume from one pump is sufficient, the flow path will be switched, increasing the horsepower consumption. It is a point. In addition, a structure that electrically detects the vehicle's running speed and uses this detection signal to switch the flow path is being considered, but the vehicle speed is not necessarily proportional to the engine rotation speed, that is, the bong discharge lid. However, it is far from being possible to effectively reduce the horsepower consumption, and there is a lot of waste. In the case of a 411 and 1 side trunk, the engine often reaches high speed rotation even when running at low speed, which is a problem, and the air condition detection means is activated by this. There are structural issues such as using magnetic valves. Furthermore, it exhibits the energy-saving effect mentioned above!
Problems in configuring the first control section
<S+ζumpt・Ratij function FF oil,
Nf: Iii fbII 1 Valve operation (i-
i 埒νt1゛improved, more --J11'l-i'
In order to improve the energy effect, this glazed flow rate control valve drains the excess pressure oil from the pump into a flow path resistance. "Words,"
- It is desirable to have a configuration that can return the circle and 1''I properly to Tanqui's law in the same 11 states, In addition, the pressure fluid supply 41:fh that requires ±5. 81 - of the pressure oil in the high rotation range of the engine has become a problem in terms of the driving performance of the car.In other words, when the car is running at high speed,... If it is too much, it will cause a sense of anxiety for the violator, so in order to eliminate the problem, it is necessary to reduce the supply amount of pressure oil to some extent!Introduce a so-called drooping mechanism. Since such a loop-pin mechanism is generally operated using the above-mentioned flow rate control valve, there is a strong demand for operational reliability of this Tltm control valve. The present invention was made in view of these circumstances, and
A pressure-sensing type flow switching pulp that operates according to the size of the fluid m device @o discharge, and an input passage switching a that operates according to the discharge from each pump and returns excess pressure body to the tank space.
It is configured to skillfully match KMU with a flow rate control pulp having i1 function to perform am switching, and also has a plurality of hole combinations K which mutually establish ffi flow paths in the R lid control pulp. Therefore, it is easy to configure #lI
This method allows us to greatly improve the operational reliability of flow rate control pulp while taking into consideration the workability, and when we install a drooping mechanism, we can also improve its effectiveness even further. In addition, by adjusting the balance between each pump and the wave body equipment, it is possible to maintain a uniform supply from the pump to the fluid equipment, so that the pump can be supplied without affecting the operation of the body equipment. ? The present invention provides a pressurized fluid supply device that can be used to reduce the fp3* horsepower and thereby further improve the energy saving effect. Below, the present invention will be explained in detail using nine practical examples shown in the drawings. FIG. 1 shows a simple embodiment of the pressure separation body supply installation according to the present invention, and in this practical example, a case will be described in which it is applied to an automobile power rudder addition &. In the figure, reference numerals 1 and 2 denote first and second pumps that discharge pressure oil separately, both of which are rotationally driven by an engine (not shown), and which transfer the hydraulic oil in the tank 3 to the flow path switching device $4. It plays the role of circulating and supplying power to the power steering device SK through the power steering device SK. It should be noted that these pumps 1 and 2 do not necessarily have to be constructed separately, and may be constructed in one piece with a common casing and pump drive shaft, but in the case of the first pump 1. It is preferable that the length of the 20th pump is also small. In addition, in the figure, 1m + 2aa is the suction side pipe of each pump 1.2, 1han is the same discharge pipe, 3a#iM
tlbc suction hook pipe 1m, 2aKJlle connected tank ll1l pipe], Kia is the pressure oil supply line 011' connecting the flow path switching mechanism 4 and power steering device 5 lever, 5h is tank 8 In order to selectively supply the pressure oil discharged from the above-mentioned first and second bongs 7''1.2 to the power steering device 5, the Ot & path switching mechanism 4 is , is composed of each member described in detail below. That is, in the figure, reference numeral 10 is a main passage for supplying O pressure oil from the above-mentioned pump 1 to the power steering system SK, and 11 is a pump 2 described in 2. A main passage 1 is provided between the main passage MIO and the sub passage 11 to which pressure oil is guided, depending on the magnitude of the load on the power steering device 5.
A pressure sensing type O flow path switching/< loop 12 is interposed which operates by sensing a change in the pressure of the pressure oil. This flow path switching valve 12Fj has a spool pulp 13 slidably supported in a pulp hole 2a having an end 111 in the shaft of the main passage 10, and this spool pulp 13 is normally supported by a spring. 14, the valve hole 12a is opened in the direction Cp of the valve hole 12a, and is spaced vJ away from the main passage 10 by the valve hole 12a. In this state, the bupu passage 11 is arranged in parallel with the bupu passage 11 via the annular groove 13m on the outer periphery of the central part of the spool pulp 13 and is connected to the 9M flow passage 15, and furthermore, the reflux conduit 15a t - It is connected to tank 3 through -. The flow path switching valve 12 has a check valve 16 at the end of the main passage 10sIII of the spool pulp 13, and the check valve 161 is moved along the 6th axis in the figure. At times, the sub passage 11rc is forced through the ligature through hole 13b and the annular vortex 13 on its outer periphery. Of course, when the flow path switching valve 12 is operated severely, the spool pulp 13 separates the two sub-patches 11 from the wound and the reflux path 15. In this state E, as long as the flow rate control valve having the flow path switching mechanism described above is in the non-operating state, the check valve teFi will not be opened by the pressure oil from the pump 2 of stripe 2. The main passage 10 has the role of merging the pressure oil from the pump 1 with the main passage 10 (see Figure 2 (A)). Tin ring 14 of IL path switching valve 12
The pressure of the tank 31i1 is led through the small hole 13d to the low pressure chamber 17 in which the pressure of the tank 31i1 is introduced, and the opposite high pressure i;
The pressure of the #j main passage 1001+1 is introduced to the 8 side through the passage 19, and the stool valve 13
When the fluid pressure in the main passage 10 rises due to an increase in the load on the power fdL extraction device 5, it senses this and moves to the right in the figure. Further, in parallel with this MLil14# valve 12 and below the main passage 10, there is a flow passage switching mechanism that senses and operates when the flow rate flowing in the main passage 10 reaches a predetermined value of 11 or more. The enemy control page 20 that does this is privately copied. This flow bar biasing valve 20 is operated when the discharge current from the first pump 1 or the discharge current from the pumps 2r) of group 2 is combined and the IAI:ll is equal to or higher than a predetermined amount. It has approximately the same configuration as the conventionally well-known t/lr, m control valve, which has the role of releasing a part of it into three tanks and maintaining the supply amount to the power rudder deck casing 5 below a certain amount. . That is, the spool valve 21 is supported in a valve hole 0a whose one end is open with respect to the main passage 1o so as to be freely energizable.
The high pressure chamber 23 defined by the front H piston valve 21 is connected to the orifice 2 through the passage 24.
2, the low pressure chamber 25 has an orifice 26m for preventing oscillation of the spool valve 21.
It is connected to the downstream side of the merifice 22 via. Then, the stool pulp 21 is placed in the high pressure chamber 23 when the stool pulp 21 is loaded by the tin ring 2T provided in the low pressure chamber 25, and in this state, the stool pulp is The connection between the main passage 1o and the tank 3 and the reflux passage 28 which communicates through the tltc pipe 28 is blocked. In addition, 29 in the figure is the stool valve 2.
This is a relief valve attached within 1. Further, as the spring 2T of the t& amount control valve 20, a spring O having a weaker biasing force than the spring 14 of the first switching valve 12@ is used. Here, the volume N control valve 20 configured as described above.
What should be noted here is that there is a bypass passage 30 that communicates with the flow path switching valve 12, and that the second pump 2 is connected to the bypass passage 30 via the sub passage 11.
This means that the pressure oil from the Normally, that is, when the waste amount control pulp is not operating, the bypass passage 30 is opened at the annular groove 21aK of the low pressure chamber 2S of the spool pulp 2-1, and is separated from the reflux passage 28. has been done. Therefore, in this state, the pressure oil from the second pump 2 is guided to the tank 3; ib or the main passage 10 according to the flow switching operation of the flow switching valve 12. On the other hand, when this flow control valve 20 is activated, as shown in FIG.
As shown in B), a part of the pressure oil that can cross the main passage 10 is returned to the tank 3 @, and the bypass passage 3
0 is the high pressure m2314 of stool pulp 21! L's Enoki #
21k, and communicates with the R flow path 2I through this. At this time, even if the flow path switching valve 12 is in the inactive state, the sub-path 111 and the return path 15 and 28 communicate with the tank 3. Then, the pressure oil from the pump 2 of #c2 returns to the tank 3Illl without any problem, but on the other hand, when the flow path switching valve 12 is activated, the ttXt passage 11 is connected to the main passage 10. The bypass passage 30 and the second switching valve 2oll are connected via the annular structure 13 to the Kiji hole 13 where the check valve 16 is installed. Therefore, in this state, the check valve 1
6 is not opened to the pressure difference on both sides thereof, and as a result, the pressure oil from the second pump 2 in the R flow passage 11 is sent to the R flow passage 28 through these two valves 12 and 20. This state is shown in the second option (0) □.The operation of the flow path switching mechanism 4 configured in this way is determined based on the discharge lid of each pump 1#2, that is, the rotation speed of the engine. Regarding the relationship with the power steering system S, first of all, in Figure 1g1, the engine reflex 0 rotation speed is low and the power rudder IIR device 5 is in an inactive state, that is, there is no load on the power steering system fk5. This shows a case where the fluid pressure in the main passage 10 is low.In this state, both valves 1
2.20 both maintain the J1 operating state, and the pressure oil from the first pump 1 passes through the main passage 10 to the power steering pump t.
t, 5, but the second pump 2 is supplied to the sub passage 11
, is connected to the tank 3 via the return path 15, and the pressure oil is supplied to the second
Pump 2. It circulates through tank 3 and is maintained in an unloaded state. This is because, even if the supply amount of pressure oil is small, the power steering device 5 is not affected by #-i at all. The capping characteristics in this state are shown in the third prisoner's solid brain W a,
Further, the horsepower consumption due to this is shown by the broken line a in Figure 4, and may be about half or less than that of the conventional system (see the two-dot chain line already shown in the figure). In addition, in FIG. 3, r is the discharge amount of the first pump, and Ps is #
! Discharge cover of pump 2, P, +P, O joint' discharge resistance -
This is a straight line showing the relationship between and N rotation. In addition, the power rudder deck [5
When the heavy load increases due to the operation of the
As shown in FIG. Therefore, zero pressure oil from the second pump 2 flows through the main passage 10.
Inside, it joins the pressure oil from No. 10 pump 1, and the power steering system*
F
1. There is no problem with the movement. The flow when this load is large! The third prisoner has a solid brain, and the consumption horsepower P
As shown in 1kan 41ffl, it is East Line C.
The dashed dotted line ε shown in 1) and the month -. Of course, in this state, the horsepower consumption cannot be reduced. Also, the pump discharge fL is times! At high speed and low pressure, when the number of pulps increases beyond the amount of pulp and the power steering device 1t5 is inactive, as shown in Figure 2 (B), the flow rate control pulp 20 is The oil from the pump 1 of Yu 1 that operates and flows through the main passage 10 is transferred to the reflux passage 28.
When the flow path switching pulp 12 is in a non-operating state and the pressure oil from the second pump 2 is It returns to the tank 3 via the nub passage 11 and the reflux passage 15. Of course, part of it is the Fi pipe passage 11 and the flow rate control pulp 20.
The water returns to the tank 3 via a reflux path 28 that communicates with the water through the tank 3. The flow characteristics in this state are shown in Figure 3! I a t or b and the corner points x and y are shown as continuous real lines, and the consumed horsepower is SI'; Broken in Figure 4? As shown by M4 &, it is sufficiently small.1 Furthermore, when the power steering device M5 operates during this high speed rotation and a pressure build-up occurs, the direction switching valve 12 is also activated, as shown in Fig. 2 (0). The sub passage 11#'i is in operation together with the flow rate control pulp 20, and as a result, the O pressure oil is guided from the 20th pump 2 to the sub passage 11#'i. 28 and communicates with the tank 3@. Then, the pressurized oil returns to the tank 3 without opening the check valve 16, and on the other hand, a part of the O pressure oil from the first pump 1 in the main passage 10 is also returned to the flow control valve 20 and refluxed. The passage 2I returns to the tank 3, and as a result, a certain amount of pressure oil is supplied to the power steering device 5. In this case, the fluidity is 3ν1
fjlc, and the horsepower consumption is shown by a solid line continuous to the Sk line in Fig. 4, which is different from conventional
It may be about half that of d).
), Pl indicates the first pump 1, Pl indicates the second pump 2, P indicates the tank 3, and P, 1 indicates the power pump 5, respectively. The above-mentioned Honkase f! The energy saving effect at +1° becomes clear from the relationship diagram between horsepower consumption and pump discharge pressure shown in FIG. First, when the pump rotation speed is in the low speed rotation range, as shown by the solid line a, in the no-load state, the horsepower consumption is about half that of the conventional system (as indicated by the two-dot chain line bh in the figure), and the load increases. Then they become the same. In addition, in high-speed rotating mounds, as shown by the east line -, the power consumption is approximately the same as the conventional method (see button d in the figure). This means that at high speeds, the first pump 1
This is because only the pump 2 is involved in supplying hydraulic pressure to the power steering device 5, and the pump 2 in the shaft 2 is not involved. Now, according to J. and the Town, as mentioned above, part of the O pressure oil from the first pump 1 in the main passage 10 and the pressure oil from the second pump 2 are transferred at high speed and high pressure. , tank 3
The reflux passage 28 of the koji valve 20, which controls the flow rate of 1tflKffitAL, has % mold in the reflux path 28, which is configured by a combination of a plurality of mutually independent holes. That is, conventionally, as this type of reflux path, generally the set 6 is used.
Although a hole 31 having a circular cross section as shown in the figure is used, if such a circular return flow path 3°1 is applied to the above-described device, the following problems will occur. A simple example of this using FIG. 0
1 to the right 0111 in the figure, and a part of the pressure oil in the main passage 10 is returned to the tank 3111 via the reflux passage 31. As the pressure oil lid increases, the spool pulp 21 gradually moves to the right side, and the flow area #i of the main passage 10, that is, the first pump 1 and the reflux passage 31 increases sequentially, but on the other hand, the bypass The opening area of the pressure oil from the second pump 2 introduced through the passage 30 to the return passage 31 gradually decreases, thereby increasing the passage resistance on the second pump 2 side and reducing the energy consumption. This will result in a loss. In the past, in order to eliminate such a problem, #'i
, there is a fee to select a shape f that alleviates the increase in flow path resistance of the pressure oil flow path from the second pump 2 with respect to the movement of the school pulp 21 to the right side, as shown in FIG. 8(^)K. As shown in the same figure (B
), a generally rectangular cast hole 33 having a length SL in the axial direction of the pulp hole 20m can be considered. However, in the former case, while the overflow timing accuracy (indicated by the dimensions in the figure), which is a problem with this type of return passage 31, can be obtained, it is difficult to cut a portion of the hole when drilling the second hole. : iU Because there are parts without L, the cutting force becomes unstable in the circumferential direction and breaks &! 9J l'ltl, which is not preferable from the viewpoint of workability, the tool life, and the hole size. In the latter case, the acid form processing is easy and the shape can be made into any desired shape, but on the other hand, the above-mentioned dimension n degree cannot be obtained. Furthermore, if the pore diameter of the reflux path 34 is enlarged as shown in FIG. Therefore, according to this example, the return flow path 28 is formed at the same location in the axial direction O of the pulp hole 20m, which is independent from the small diameter path 211m machined and which can obtain overflow timing accuracy. It is composed of a cast hole 2@b having an abbreviated shape and having a mever-wrap portion (indicated by dimension t in the figure). In addition, 3s in the figure is a ball that closes the seven-pronged hole during processing of the small-diameter passage 28a.1 And, according to such a configuration, pulp production is carried out in the small-diameter passage 29m constituting the return path 2$. timing of time 8
If you can get K, you can easily move the force: [,
The presence of the cast hole 28k that can be formed by the pump 2t of the pump 2t of the pump 28k eliminates problems such as the Mt channel of the pump 2t of the pump 2t being constricted by the pulp action and increases the flow channel resistance, thereby ensuring a sufficient opening area. , energy saving effect *t- can be achieved. This is indicated by the solid line a in Figure 10.
．． It will be clear from the characteristic curve of the overflow passage opening rkr nucleus. In addition, the broken line in the same figure shows the case of a single circular passage, and the fine magnet C in the same figure shows the case of a combination passage with a person and a small diameter hole, respectively. In particular, according to this example, the diameter of the passage other than the small diameter passage 28a, which requires timing accuracy, can be easily and inexpensively made into a cast-open large 28b, which is of a type 1+k. □It is possible to obtain a □ shape, which has great advantages. However, this proposed plan is limited to the ``swimming path 28'' which is a combination of the above-mentioned machined small path 28m and the tuna extraction hole 28b. A variant is given an audience. In the embodiment shown in Figure ksl1, for the valve hole 20aK,
Reflux Td836 consisting of a small diameter passage 36 & and a large diameter passage 36b drilled from opposite directions with a drill etc.
, a part of which is formed in the valve hole 20a.
The Ikll is formed so as to overlap in one direction, and the main timing screen is obtained in the small diameter passage 36alJ&.In such a configuration, the passages 36a and 36k touch each other. Therefore, no problem arises in terms of workability.In addition, in the embodiment shown in FIG.
It is easy to understand that the same effect as described above can be obtained even in this case. Figure 13 #' shows another example of the pressure fluid supply device according to the present invention. Therefore, detailed explanation thereof will be omitted. In the figure, P11 is the first pump 1, Pl is the second pump 2, '1' is the tank 3, p
The power steering device 5 is shown as an i+li fluid device. i-c, the difference in the apparatus of the present example is that a drooping mechanism is attached to the flow control pulp 20. In other words, the pressure oil from the first pump 1 is transferred to the power vessel. In the middle of the main passage 10 that supplies to the main passage 10, there is a cut orifice 22Fi above flow) 41irll gon valve 2
The main passage 10 is opened to the low pressure 42rM in the valve hole 20a of the pulp hole 20a.
The pulp hole 20m is configured to pass through the pulp hole 20m through the low pressure chamber 274AJK of the spool valve 21 inside. And this flow M control pulp 20
The stool valve 21 on the left side in the figure due to the operation of
During the movement of
The V.
The so-called ``mouth that performs a drooping action'' is formed by five oriais. is possible. In addition, in the fi path switching pulp 12, in order to bias the spool valve 13 to the high pressure 'M18@J of the valve hole 12m, a large spring 14m and a small 2114M spring,
14B is used to buffer the problem caused by the pressure oil from the m2 pump 2 suddenly joining the main passage 10 when the stool valve 13 is activated, causing an excessive pressure rise. 1, that is, the spool pulp 1 by the above-mentioned large and small springs 14mm@14''
The biasing force for 3 exhibits a non-linear characteristic and plays a role in slowing down the tight movement of the spool valve 130. Further, the rectangular #l113 formed in the low pressure chamber 1711 of the land portion 13d of the spool valve 13 also plays a similar role. In addition, 13f in the figure is a rod portion that regulates the amount of moss movement of the stool valve 13. The &pupil with the above-described configuration operates as follows. 1. In the 13th ν1, the engine rotation speed is low and the power steering device 5 is in an inactive state, that is, the power steering device j [
4f115K This shows the case where no load is applied and the fluid pressure in the main passage 1° is low pressure. In this state, both pulps 12.20 remain inactive, resulting in a
The pressure oil from the first pump 1 is supplied to the power steering device 5 through the main passage 10, but the second pump 2 is supplied to the power steering device 5 through the sub passage 1.
1. It is connected to the tank 3 via the reflux path 15, and the pressure oil circulates through the second pump 2 and the tank 3 to maintain an unloaded state. This is because if the supply amount of pressure oil is small, the turtle power rudder augmentation device 5 will not be able to function at all. In this state, the tlLll% performance 1.1 is shown by the middle line a in Fig. 15, and the horsepower consumed by K is shown by the middle line a in Fig. 16. ) should be about half or less. In addition, the discharge force of the 15th [middle pttt first pump 1, P
I is the discharge vibration of pump 2 of bacteria 2, P1+F is the sum 1
1 is a graph showing the relationship between discharge and pump rotation speed. In addition, the center line in Fig. 15 is the horsepower consumption of the first pump 1, 'j is the horsepower consumption of the second pump 2, and Pg +'s/
ri that total rt! This is a straight line that represents the relationship between horsepower, pump rotation speed, and O. On the other hand, when the load increases due to the operation of the power steering increase device 5 from the low speed and low pressure state shown in FIG. 13, and the state becomes low speed and high pressure, tILw! The t8II exchanged pulp 12 is activated and the second pump 2. 4A between 3 tanks
and connect the second pump 2 to the main passage 10 via the check valve 16. Therefore, the O pressure oil from the second pump L-O joins the pressure oil from the Ml pump 1 in the main passage MIO and is supplied to the power rudder MR system [5 to generate the necessary steering operation assisting force. , there is no problem in operation. The center line in Figure 15 shows the power consumption when the engine load is large, and the horsepower consumption is shown by the solid line in Figure 16. (see). Of course &1, it is not possible to reduce horse consumption in this state. In addition, in a high-speed, low-pressure situation where the pump discharge m increases to a predetermined amount or more with the rotation speed and the four-stroke power steering augmentation device 5 is inactive, as shown in Fig. 14-), The flow lft control pulp 2o is actuated to release a part of the pressure oil from the first pump 1 flowing through the main passage INIto to the tank 3flIIK via the recirculation passage 28, and the supply lid to the power steering device 5 is closed. The pressure is controlled to be constant, and the drooping effect of the large-diameter portion 40 of the stepped annular groove 4o that narrows the orifice 22 reduces the supply amount and maintains it at a constant amount in the rough FCHi positioning. At this time, Yodo IjI! 1 switching pulp 12
is not in operation, and the pressure oil from the second pumps 27) returns to the tank 3 through the sub passage 11 and the reflux passage 15. Of course, a part of it returns to the tank 3 via the ffi channel 28 which communicates with the tube channel 11 via the miscarriage control valve 2o. This was the situation. The swimming cap characteristics are shown in Fig. 15 by solid lines C and d that are continuous with the solid line a and the corner points X and Y, and the horsepower consumption is sufficiently small as shown by the center line a in Fig. 15. During this high-speed rotation, press the
5 is activated and the pressure is maintained, as shown in Figure 14 (0), tlL'#! The I-switching pulp 12 is also in operation along with the flow control pulp 20, so that the second pump 2
As described above, the tube passageway 11 to which the pressure oil is guided is connected to the reflux passage 211 via the bypass passage 30 and the RJllIKIIll/(Lube 20C) II-shaped groove 20k, and communicates with the tank 31411. Then, the O pressure oil is returned to the tank 31IilK without releasing the check valve 16, and on the other hand, -fJ of the pressure oil from the Ayu 10 pump 1 in the main port *10 is also returned to the Oa amount control knob 2. (Hζ returns to the tank 31tllK, and as a result, a certain amount of pressure oil is supplied to the power steering device 5. At this time, q) The flow rate characteristics are shown by the Chinese line in Figure 15, and the horsepower consumption is 16 In Fig. 1, it is indicated by * + tJo followed by actual time, and this is Fi conventional (
The middle damage (Md) in the same figure may be about half as wide. The energy saving effect of the above-mentioned actual AN device becomes clear from the relationship between the horsepower and the pump discharge pressure shown in Figure &1117. First, the subcommittee where the pump synchronization F1 is a low-speed subtransfer, Souki A
As shown in Figure 1, under no-load conditions, the conventional
b & teru), it is 18 responsibilities for about 4 hands, and it becomes the same when the shell cargo is accumulated. tfc
This is ilO regardless of the magnitude of negative 1iJ during sieving.
This is because the pump 711Z) is involved in freezing the hydraulic pressure to the power steering device 5, and the pump 2 is not involved. . Now, the above-mentioned Jin no Ou 1; is example 1. -4 also,
Similar to the discussed fire k 11v, flow i control wholesale pulp 2o
The return path 28 is composed of a combination of mutually independent and modulus holes. Then, such an empty number f:, b! , for example, the small diameter passage 281L shown in stripes 9t>4+(^)(B) and the traversed ηL path 2 by the pongee strip light hole 28b.
0 represents the effect of the following Q°. In other words, what is needed is that the movement of the spool valve 21 is controlled by the pressure oil from the first pump 1. Even when the specific discharge t1tm of the engine is small, the OJ variable orifice, which performs the looping action by displacing it as much as possible, must be appropriately throttled and configured to improve its operability. Then, in order to secure the ffi flow path for the O pressure oil from the second pump 2, it is necessary to secure the ffi flow path for the O-pressure oil from the second pump 2. 20 & 1! if
hJd hole 2 with a large opening on the low pressure rich 2T side in the shielding direction
According to 2ii Ryupai 28 consisting of 6k, 11: (O plate 1
In addition, in iwIt with the above-mentioned configuration, when the rotation LJ exceeds N1, the pump 2 of the navy blue 2 is always connected to the tank 3, and the main ground 10 This is less than about half of the amount of ml electric Z/tsu'jK, which reduces the change Ei of 41 rice LIIW pulp 200 pulp, and requires countermeasures as described in IaJI.・t 1tvILj;l52 as described above.
According to J1, as shown by the solid border in Figure 18, compared to the conventional general circular passage (indicated by broken noodles), we hope that it will be more effective. Ko04. In this case, J in the figure shows the characteristics of the shape Q4, which is a combination of a person and a small passage hole. So-〇, characteristically, it is Honjima J! Although it is somewhat similar to that of
In terms of workability as described above, if the pulp displacement becomes large, the opening area (as in the present invention) becomes small, which is unfavorable in terms of operation. Further, in the reflux passage according to the present invention, the shape of the hole for removing force can be freely changed by arbitrarily selecting the shape of the hole for removing force, which is a great advantage. In addition, in the above-mentioned embodiment, the reflux path in the pulp of stream 111J is defined as 1 for a combination of two holes, but the present invention is not limited to this, and the numeral It is easy to understand that the number of rings should be determined by matching the redness of the holes in the pump. As for the case in which hydraulic pressure is connected to pump 5, the present invention uses "V" (prohibited) pumps, one of which is the main pump, and the remaining pumps are sequentially connected to the pump and Jζ/p. Needless to say, it is also possible to use a main passageway with a structure that can be separated and separated.Furthermore, the pressure fluid supply device according to the present inventor and Akira can be read by cutting off each middle part. The shape, structure, etc. of A pressure-sensing fItM switching pulp that operates according to the size of the supply passage, and a violet control pulp that has a kII6 switching function that operates according to the discharge lid from each pump and releases excess pressure fluid into the tank. In addition to skillfully combining these methods, the flow return path in the flt'11 control pulp is constructed by combining and combining multiple holes carved into Japanese roof tiles, resulting in a simple structure with excellent workability. Regardless of the situation, the flow rate control pulp can be operated properly and reliably, and the 7 AII control functions can be demonstrated. In addition, according to the present invention, the addition of the drooping mechanism has five advantages in that the effects can be quickly and properly exerted.Furthermore, This is the start! 4#J is equipped with multiple pumps for supplying O pressure fluid to the d1 fluid-device. One pump is used as the main pump, and the remaining pumps are used as supplementary pumps. Since it is configured to be selectively disconnected from the fluid equipment supply path by the IT switching mechanism, the minimum required pressure fluid is supplied despite the simple configuration, and energy loss was previously considered to be avoided. Eliminate waste, rl
'! There are nine advantages that can further reduce horsepower costs, save energy, and maintain a proper operating condition without affecting the fluid equipment in any way. Further, according to the present invention, the &ji! It has a structure that skillfully combines IFIJ-controlled pulp, has a simple structure, can be manufactured using GJIK, and has the advantage of being expected to make the entire device lighter and more compact.

[Brief explanation of the drawing]

, Figure 1 is a system diagram showing an embodiment in which the pressure body supply device according to the present invention is applied to the power steering system, and the second IM
(A) (ml) (0) is an explanatory diagram showing its operating state, Fig. 3 is a % property diagram showing vL'M% property, Fig. 4 and 5
The figure is a characteristic diagram showing the relationship between horsepower consumption, pump rotational speed, and pump discharge pressure. )
Fig. 1) is a plan view and a side view showing an embodiment of the R11l path to which the present invention is projected, Fig. 1θ is a flaw diagram showing the relationship between the overflow passage opening area of the pump pump and the valve displacement, and tg11 Figures 1 to 12 are a plan view, a sectional view, and a schematic view as seen from the direction of arrow 0, showing modified examples of the return flow path,
Figures 1@13 and 14 (A), (B), and (0) are system diagrams showing other embodiments of the present invention, and Figures 15 to #g17 show flow characteristics, pump rotation speed, horsepower consumption, and pump rotation. number,
Characteristic diagram showing the relationship between horsepower consumption and pump discharge pressure, No. 18
The figure is a characteristic diagram showing the relationship between the overflow passage opening area and the valve displacement.1...Hall 17Z) pump, 2...#A2 pump, 3...tank, 4...flow path Cut IA mechanism, 5
...Power steering device (i-body equipment), 1...--7
47 passage, 11...Nap passage, 12...f4L
Road cutting torsion valve, 15...reflux path, 16...check valve, 20...#l'jl control valve, 22...
Orifice, 28... ffi boiled sweetfish, 28 hatake...
Small tγ passage, 28b is 00 pistol extraction hole, 29...relief valve, 30...bypass passage, 36.31...
・Return path, 36m, 36b; 37m, 37k ・Fist・
Fist-sized, small diameter passage, 40.Fist...Stepped stacked shape, 40a.-
・Working large diameter part. %r1 Out # In/out 0 Personnel Vehicle Equipment Co., Ltd. Agent Masaki Yamakawa (and 1 other person) Figure 1 Figure 2 (C) Figure 3 Figure 4 Figure 5/Funfusuyu 41p Chapter 6 Figure 7 (A) Figure 7 (B) [ 5 - Figure 10 Figure 12 (A) +4 Figure 15 Figure 16 Figure 17 Figure 1B Procedural amendment (voluntary) 1982 patent application No. 72997 Ci'' 2, Name of the invention Pressure transfer body supply device 3, Supplement 11-Relationship with matter 1) Patent Applicant name (name) Automotive Equipment Co., Ltd. ■ Specification, page 33, line 8 l Take the pulp l. Correct it with "Pulp". (2) Figures 4, 5, and 11) are corrected as shown in the attached sheet Yy. Above 2- Figure 4 Figure 5

Claims (1)

[Claims] (1) A first and second pump that separately discharges pressurized fluid, a main passage that supplies pressurized fluid from the first pump to the fluid equipment, and a main passage that is disposed in the middle of this main passage O and is always on. a spool that connects the second pump and the tank and that is activated by an increase in the load of the fluid device to disconnect the second pump and the tank and connect the second pump to the main passage; a spool which is connected to a flow path switching nozzle in the middle of the main passage and which returns part of the pressure fluid from the first pump or the pressure fluid from the Tuna 1 and Rattan 2 pumps to the respective tanks; A flow control pulp having a flow rate control pulp, and a valve hole that slidably holds the spool of the flow control valve has a DRIL path to a tank configured by a combination of mutually independent holes. Pressure fluid supply pipe WIt, which is slightly opened, (first and second pipes that separately discharge warm pressure fluid)
a pump, a main passage for supplying pressure fluid from the first pump to the fluid equipment, and a main passage arranged in the middle of the main passage and normally connecting the second pump and the tank and on the fluid equipment side. a flow path isolation valve having a spool that is actuated by an increase in load to isolate the second pump and the tank and connect the second pump to the main passage;
a flow rate control pulp having a spool connected in the middle of the main passage and causing a part of the pressure fluid from the pump @1 or the pressure fluid from the first and second pumps to flow into a tank @K 111fi, respectively; The valve holes for slidably holding the flow control pulp spool are provided with a variable orifice that performs a trooping action by constricting the front main passage according to the amount of movement of the spool of the side pulp. A return flow path to the Tarek side, which is configured by a combination of the number of holes, is opened.
-Featured pressure fluid supply device.