JPH0688567A - Hydraulic flow synchronizer - Google Patents

Abstract

PURPOSE:To secure the extent of synchronization for normally stabilized separate flow in a simple structure using no valve gear by reciprocating a piston by means of rotation of a cylinder barrel via a swash plate mechanism, while connecting plural supply and exhaust ports and a connecting passage respectively in a specified state. CONSTITUTION:When an on-off valve 102 is seelcted and pressure oil out of a supply source 101 is fed to a first external connecting port 160 in a hydraulic flow synchronizer 100, this pressure oil opens a check valve 183 and flows down to respective supply and exhaust ports 143, 142 of a cover 112 from a first connecting passage 170. In addition, this pressure oil rotates a cylinder barrel 116 according to a tilt angle of a swash plate 117, and it functions as the same capacity double motor consisting of a cylinder hole 121 and a piston 131 in a first group and a cylinder hole and a piston in a second group. In consequence, since the pressure oil flows down simultaneously at the same quantity to respective actuators 103a, 103b, these identical rated ones 103a, 103b are elongated at the same speed.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic flow rate tuning device for uniformly holding each split flow rate in a hydraulic split circuit.

[0002]

2. Description of the Related Art In a hydraulic circuit, for example, in order to operate two actuators at a constant speed in synchronization, it is necessary to devise to divide the pressure oil supplied from a pressure oil source at an always uniform flow rate. Conventionally, in order to meet this type of demand, the flow rate of one circuit is compensated for by the various valve devices.

[0003]

However, in the conventional method, since the flow rate is tuned by the valve device, the structure of the valve device is complicated, the adjustment is complicated, and the tuning is out of sync when the load changes. A flaw is pointed out.

An object of the present invention is to avoid a system using a valve device which has a complicated structure, and to tune the diverted flow rate which is always stable regardless of load without adjustment, regardless of a special structure. An object is to provide a hydraulic flow rate tuning device.

[0005]

In order to achieve the above-mentioned object, in the hydraulic flow rate tuning device according to the present invention, the shaft is located at a position on the same eccentric radius in a cylinder barrel rotatable about the shaft center. An even number of cylinder holes of the same diameter arranged in parallel so as to surround the heart, an even number of pistons slidably inserted in each of the cylinder holes, and in the pistons as the cylinder barrel rotates. A swash plate mechanism slidably coupled to one end of each piston so as to give a reciprocating motion, and first and second cylinders each having the same number of the cylinder holes.
And a valve plate slidably coupled to one end surface of the cylinder barrel so as to form a pair of independent supply / discharge passages having different eccentric radii for each of the two groups, and the first and second via the supply / discharge passages. For each second group, a pair of supply / discharge ports for supplying / discharging oil to / from each of the cylinder holes, and a pair of ports serving as an intake side or a discharge side of these supply / discharge ports are provided as a first group. A first connection passage connected to one external connection port, and a second and third external connection ports in which the other pair of the supply and discharge ports, which is the suction side or the discharge side, is independent from each other. And second and third connection passages connected to the.

In the hydraulic flow rate tuning device according to the second aspect of the present invention, valve means is provided in the first connecting passage for giving a throttle action to the oil flowing in at least one of the directions.

Further, in the hydraulic flow rate tuning device according to the third aspect of the present invention, the cylinder barrel is configured to be freely rotatable.

Further, in the hydraulic flow rate tuning apparatus according to the invention of claim 4, the cylinder barrel is configured to be rotationally driven from the outside by a rotary shaft, and one of the supply / discharge ports which is on the suction side in the rotational driving direction. The paired ports are connected to the first external connection port by the first connection passage as an integral or separate port, and form the other pair of the supply / discharge ports that are on the discharge side in the rotational driving direction. Another port is connected to the second and third external connection ports independent of each other by the second and third connection passages.

[0009]

The basic component of the hydraulic flow rate tuning device according to the present invention is, in short, a single cylinder barrel which is an axial piston machine having double motor or double pump functions by the two groups. . For example, according to the invention according to claim 3, this functions as a double motor, and in this case, the passing oil amount of _one motor discharged from the second external connection port is Q ₁ , When the passing oil amount of the other motor to be discharged and _{Q 2, Q 1 = Nq 1} = N · Z · Πd 1 2/4 · πD · tanα Q 2 = Nq 2 = N · Z · Πd 2 2/4・ ΠD ・ tanα However, N: rotation speed, Z: number of pistons, d: piston diameter, D: piston PCD (diameter between shafts), α: tilt angle

Here, since all the pistons are incorporated in a single cylinder barrel with the same eccentric radius, N,
D and α are the same in both formulas, and since the number of pistons is the same in both groups, Z is also the same, and the piston diameter and cylinder bore diameter can be machined with extremely high precision by selecting machining tolerances. In addition, d ₁ = d ₂ can be substantially set, so that the amount of oil passing through both motors is substantially Q ₁ = Q ₂ and has the same capacity, so that the tuning action can be achieved. In this case, it goes without saying that the relationship of the above equation is established by the reciprocating flows of both motors.

The same applies to the invention according to claim 4, in which the basic component of the hydraulic flow rate tuning device is, to put it simply, a single cylinder barrel and an axial piston having a double pump function by the two groups. Since it is a pump, the discharge oil amount of _one pump discharged from the second external connection port is Q ₁ , and the discharge oil amount of the other pump discharged from the third external connection port is Q.
If the value is ₂ , the relationship between the above two expressions holds. In this case, when the reverse flow is performed by the weight of the load, it acts as a double motor, which is as described above.

According to the second aspect of the present invention, the valve means is inserted into the first connecting flow passage which is a common passage, whereby a throttle action is given to the oil flowing in at least one of the directions, and the speed of the actuator is increased. Adjust. The oil flowing in the other direction may be given a free flow or may be given an arbitrary throttling action.

[0013]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A hydraulic flow rate tuning apparatus according to a first embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 4, the hydraulic flow rate tuning device 100 according to the present embodiment includes a hydraulic power source 1
In order to divert the pressure oil introduced from 01 through the on-off valve 102 to the load actuators (single-acting cylinder piston device in the illustrated example) 103a and 103b to be synchronously driven at a uniform flow rate, a double cylinder cylinder double It constitutes an axial piston machine that operates as a motor.

The structure of the main part of the hydraulic flow rate tuning device 100 will be described with reference to FIGS. 1 to 3. In the case internal space formed by the case 111 and the cover 112, the rotary shaft 1 is provided.
13 is rotatably arranged by bearings 114 and 115, and the cylinder barrel 11 is attached to the rotary shaft 113.
6 is attached together with the rotating shaft 113 so as to freely rotate around its axis.

Inside the cylinder barrel 116, FIGS.
As shown in FIG. 5, the same caliber d is arranged in parallel at a position on the radius of the same eccentric distance D / 2 so as to surround the rotary shaft 113
Even number (here 6) of cylinder holes 121 to 126
Is provided, and the pistons 131 to 136 are provided in each cylinder hole.
Are slidably inserted.

On the piston tip side, a swash plate 117 is supported by the case 111 in a cradle shape so as to surround the rotary shaft 113, and the tilt angle of the swash plate is set to a predetermined angle. There is. The cover-side end surface of the swash plate 117 is slidably coupled to one end of each piston so as to reciprocate the pistons 131 to 136 as the cylinder barrel 116 rotates.

A cover-side end surface of the cylinder barrel 116 is slidably connected to a valve plate 119 supported by the cover 112, and the valve plate 119 is formed on radii of different eccentric distances as shown in FIG. 3a. First
And second suction ports S ₁ , S ₂ and first and second discharge ports P
₁ and P ₂ are provided. The first inlet S ₁ and the first outlet P ₁ are on the same radius D ₁ (> D), and the second inlet S ₂ and the second outlet P ₂ have a radius D smaller than D _{1. 2}
(<D) above.

FIG. 3 shows the suction port and the discharge port.
As shown in b, the cylinder holes 121, 123, 125 of the first group, which are alternately selected from the cylinder holes of the cylinder barrel 116, are provided in the first suction port S ₁ and the first discharge port P ₁ . The second group of cylinder bores 122.124.126 are likewise aligned with the second inlet S ₂ and the second outlet P ₂ . In this way, the valve plate 119 slidably connected to the one end surface of the cylinder barrel 116 forms a pair of independent supply / discharge passages having different eccentric radii for each of the first and second groups. .

As shown in FIG. 4, the cover 112 has a pair of supply / discharge ports 141 for supplying / discharging oil to / from the cylinder holes for each of the first and second groups via the supply / discharge passages. , 151 and another pair of supply / discharge ports 14
2, 152 are formed, and the ports 141 and 151 of these supply / discharge ports are both connected to the first external connection port 1
The first connection passage 170 connected to the first and second ports 60 and the second ports 142 and 152 of the supply / discharge ports are independent from each other.
And second and third connection passages 171 and 172 connected to the third external connection ports 161 and 162.

A valve device 180 is mounted on the cover 112 as shown in FIGS.
Includes a first valve device 181 inserted into the first connection passage 170 and a second valve device 184 connected between the second and third connection passages as shown in FIG. There is.

The first valve device 181 is a throttle valve 182.
And the check valve 183 are connected in parallel, and the check valve 183 is opened for the inflow pressure oil from the first external connection port 160 to give a free flow, and conversely, it flows out to the first external connection port 160. It is a non-symbol valve that gives a throttle action preset by the throttle valve 182 to the pressure oil flow.

The second valve device 184 is the actuator 10
A correction valve for aligning 3a and 103b, in which a parallel circuit of a pair of relief valves and a check valve is connected face to face. This is because when one of the actuators reaches the stroke end first, the increase of its load pressure opens one relief valve to supply all the pressure oil to the other actuator and immediately to the stroke end. This is to achieve the function of absorbing the displacement of both actuators as soon as possible.

The hydraulic flow rate tuning device of the first embodiment is used, for example, when two actuator cylinder devices are operated synchronously with the pressure oil supplied from a single hydraulic unit in order to move the lift deck up and down. .

That is, when the on-off valve 102 is switched to supply the pressure oil from the pressure oil supply source 101 to the first external connection port 160 in FIG.
3 is opened to flow into the supply / discharge ports 141 and 142 of the cover 112 from the first connection passage 170, and the cylinder barrel 116 is rotated in accordance with the tilt angle of the swash plate 117, thereby
Cylinder holes 121, 123, 12 forming a group of
5 and pistons 131, 133, 135, and cylinder holes 122, 124, 126 and pistons 132, 134, 136 forming the second group, and function as a double motor of the same capacity.

In this case, the second external connection port 16
Assuming that the amount of oil passing through one motor from Q1 is Q ₁ and the amount of oil passing through the other motor from the third external connection port 162 is Q ₂ , then Q ₁ = Nq ₁ = N · Z ^{_{· Πd 1 2/4 · πD}} · tanα Q 2 = Nq 2 = N · Z · Πd 2 2/4 · πD · tanα where, N: rotational speed, Z: piston number, d: diameter of the piston, D: piston PCD (Diameter between shafts), α: Tilt angle

Here, since all the pistons 131 to 136 are incorporated in the single cylinder barrel 116 with the same eccentric radius D / 2, N, D and α are common to both formulas,
In addition, since the number of pistons is the same in both groups, Z is also the same number, and since the piston diameter and the bore diameter of the cylinder hole can be machined with extremely high precision by selecting the machining tolerance, this is also substantially d ₁ = d ₂ = Therefore, the amount of oil passing through both motors becomes substantially Q ₁ = Q ₂ and has the same capacity, so that the tuning action can be achieved. In this case, it goes without saying that the relationship of the above equation is established by the reciprocating flows of both motors.

As a result, the actuators 103a, 1
The same flow rate simultaneously flows through 03b, and the actuators 103a and 103b having the same rating extend at the same speed. When the on-off valve 102 is returned to the state shown in FIG.
2nd and 3rd by the load applied to 3a and 103b.
The pressure oil that returns to the external connection ports 161 and 162 of the above reversely flows into the supply and discharge ports 151 and 152, and similarly, the double motor is rotated to cause the first connection passage 170 from the common first connection passage 170 through the throttle valve 182 to External connection port 160
And flows out to the tank 190 via the on-off valve 102. In this case, the lowering speed of the actuators 103a and 103b can be set by adjusting the throttle opening of the throttle valve 182.

5 to 7 show a hydraulic flow rate tuning device according to a second embodiment of the present invention. In this example, unlike the first embodiment, the rotary shaft is rotationally driven from the outside to form a double piston. A functioning axial piston machine is constructed. 5 to 7, parts having the same or similar effects as those of the first embodiment described above are designated by the same last two digits.

The main part of the second embodiment different from the first embodiment is that the cylinder barrel 216 is configured to be driven to rotate by a motor 220 connected to a rotating shaft 213, and a swash plate 217. Is a discharge amount setting rod 218 whose axial position can be adjusted by screw operation from the outside.
a) and 218b, the tilt angle is variably set, and the suction ports S ₁ and S ₂ provided in the valve plate 219 are formed as one common suction port S. The point is that the first supply / discharge port 241, 242 is connected to the first external connection port 260.
The second valve device 284 is different from the first embodiment in that
A connection point between a pair of relief valves respectively interposed between the tank line and the third connection passage and the tank line is dropped to the tank line. The suction ports S may be separate suction ports as in the first embodiment.

The hydraulic flow rate tuning device of the second embodiment is also used when the hydraulic oil from the tank 290 is supplied to two actuator cylinder devices to move the lift deck up and down by a double pump operation for synchronous operation. It is possible.

That is, in FIG. 7, when the motor 220 is operated to drive the cylinder barrel 216 to rotate in one direction by the rotary shaft 213, the cylinder holes 221, 223, 225 and the piston 23 forming the first group are formed.
1, 233, 235 and cylinder holes 222, 224, 226 and pistons 232, 2 forming the second group.
A pair of axial piston pumps 34 and 236 function as a double pump having the same capacity according to the tilt angle of the swash plate 217, and the pressure oil in the tank 290 passes from the first external connection port 260 through the check valve 283. Then, the second external connection port 261 and the third external connection are sucked into the supply / discharge ports 241 and 242 of the cover 212 from the first connection passage 270 and have the same discharge amount according to the tilt angle of the swash plate 216. From the port 262 to each actuator 203a,
It is supplied to 203b.

In this case, the second external connection port 26
Assuming that the discharge oil amount of _one pump discharged from ₁ is Q ₁ and the discharge oil amount of the other pump discharged from the third external connection port 262 is Q ₂ , Q ₁ = Nq ₁ = N · Z ^{_{· Πd 1 2/4 · πD}} · tanα Q 2 = Nq 2 = N · Z · Πd 2 2/4 · πD · tanα where, N: rotational speed, Z: piston number, d: diameter of the piston, D: piston PCD (Diameter between shafts), α: Tilt angle

Here, since all the pistons 231 to 236 are incorporated in the single cylinder barrel 216 with the same eccentric radius D / 2, N, D and α are common to both formulas,
In addition, since the number of pistons is the same in both groups, Z is also the same number, and since the piston diameter and the bore diameter of the cylinder hole can be machined with extremely high precision by selecting the machining tolerance, this is also substantially d ₁ = d ₂ = Therefore, the amount of oil discharged from both pumps becomes substantially Q ₁ = Q ₂ and has the same capacity, so that a tuning action can be achieved.
In this case, it goes without saying that the discharge amounts of both pumps can be arbitrarily set by changing the tilt angle α of the swash plate 216 by adjusting the axial position of the rods 218a and 218b.

In this way, the actuators 203a,
The same flow rate simultaneously flows through 203b, and the actuators 203a and 203b having the same rating extend at the same speed. When the connection between the motor 220 and the rotary shaft 213 is disconnected by, for example, a clutch, the second and third external connection ports 26 are generated by the loads applied to the actuators 203a and 203b.
The pressure oil returning to 1, 262, on the contrary,
252, and in this case, the cylinder barrel 216 is rotated as a double motor to rotate the common first connection passage 2
Pressure oil flows from the first external connection port 260 to the tank 190 via the throttle valve 282. Also in this case, the lowering speed of both actuators 203a and 203b can be set by adjusting the throttle opening degree of the throttle valve 282.

As a modification of the second embodiment, if the motor 220 is a reversible rotary motor, the actuator can be both raised and lowered by driving the motor. In addition, the motor 22
Even if 0 is a motor that rotates in a constant rotation direction and the tilt angle of the swash plate 217 is switched to a reverse tilt, a forward / reverse pump can be used, and the supply and discharge directions of the pressure oil can be switched.

In the second valve device 284 as the correction valve in the second embodiment, when either one of the actuators reaches the stroke end first, the discharge pressure oil corresponding to that amount is transferred from the relief valve to the tank 290. The pump discharge pressure oil is supplied to the other actuator only to the other actuator, and the function of aligning both actuators at the stroke end is fulfilled.

As described above, according to the present invention,
A hydraulic flow rate tuning device that can tune the flow rate without using a valve device that has a complicated structure can be realized at the technical level of a general piston motor or piston pump without using a special structure, and a complicated valve. It is possible to obtain a hydraulic flow rate tuning device which requires almost no adjustment and is capable of always performing stable tuning of the divided flow rate regardless of the load without any adjustment.

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing a configuration of a main part of a hydraulic flow rate tuning device according to a first embodiment of the present invention.

FIG. 2 is a rear view showing an end face on the cover side of the hydraulic flow rate tuning device according to the first embodiment as well.

FIG. 3 is a detailed view of a main part in the first embodiment, in which a is a schematic end view showing a port configuration of a valve plate, b is a schematic end view showing a port configuration of a valve plate side end face of a cylinder barrel, and c is a schematic end view. It is a longitudinal cross-sectional view of a cylinder barrel.

FIG. 4 is a hydraulic circuit diagram showing an example of use of the hydraulic flow rate tuning device according to the first embodiment.

FIG. 5 is a vertical cross-sectional view showing a configuration of a main part of a hydraulic flow rate tuning device according to a second embodiment of the present invention.

FIG. 6 is a schematic end view showing an example of the port configuration of the valve plate in the second embodiment.

FIG. 7 is a hydraulic circuit diagram showing a usage example of the hydraulic flow rate tuning device according to the second embodiment.

[Explanation of symbols]

 100, 200: Hydraulic flow rate tuning device 113, 213: Rotating shaft 115, 215: Valve plate 116, 216: Cylinder barrel 117, 217: Swash plate 119, 219: Valve plate 121-126: Cylinder hole 221-226: Cylinder hole 131-136: Piston 231-236: Piston 141, 151: 1st group supply / discharge port 241, 251: 1st group supply / discharge port 142, 152: 2nd group supply / discharge port 242, 252: 2nd group Supply / discharge port 160, 260: first external connection port 161, 261: second external connection port 162, 262: third external connection port 170, 270: first connection passage 171, 271: second Connection passage 172, 272: Third connection passage 181, 281: Valve device

Claims (4)

[Claims] 1. An even number of cylinder holes of the same diameter, which are arranged in parallel so as to surround the shaft center at positions on the same eccentric radius in a cylinder barrel rotatable about the shaft center, and each of the cylinder holes. An even number of pistons slidably inserted and a swash plate mechanism slidably coupled to one end of each piston so as to give a reciprocating motion to the pistons as the cylinder barrel rotates. A valve plate slidably coupled to one end surface of the cylinder barrel so as to form a pair of independent supply / discharge passages having different eccentric radii for each of the first and second groups of the cylinder holes; A pair of supply / discharge ports for supplying / discharging oil to / from the cylinder holes for each of the first and second groups via the supply / discharge passages, and a suction side or a discharge side of these supply / discharge ports. The first connecting passage that connects one pair of ports to the first external connection port and the other port that forms the other pair, which is the intake side or the discharge side of the supply / discharge ports, are independent of each other. And a second and a third connection passage connected to the second and the third external connection ports. 2. A hydraulic flow rate according to claim 1, wherein a valve means for giving a throttling action to oil flowing in at least one of the directions is inserted into the first connection passage. Tuning device. 3. The hydraulic flow rate tuning device according to claim 1, wherein the cylinder barrel is configured to be freely rotatable. 4. A rotary shaft for rotationally driving the cylinder barrel from the outside, wherein one pair of ports of the supply / discharge ports, which are suction sides depending on the rotational driving direction, are integrated or separate ports. Another port that is connected to the first external connection port by the first connection passage and that forms the other pair of the supply / discharge ports on the discharge side depending on the rotation drive direction is the second and third ports. The hydraulic flow rate tuning device according to claim 1, wherein the hydraulic flow rate tuning device is connected to the second and third external connection ports independent of each other by a connection passage.