WO1997007878A1

WO1997007878A1 - Drive device for disintegrating mixer

Info

Publication number: WO1997007878A1
Application number: PCT/JP1996/002459
Authority: WO
Inventors: Hiroshi Shimizu
Original assignee: Komatsu Ltd.
Priority date: 1995-08-31
Filing date: 1996-08-30
Publication date: 1997-03-06
Also published as: DE19681540T1; KR970009892A; JPH0966226A; JP3358774B2; KR100341137B1

Abstract

A disintegrating mixer comprises a plurality of rotors (3, 5, 7) rotatably provided in a housing (1), and respective oil hydraulic motors (2, 4, 6) for driving the respective rotors. Outlet ports (6b, 2b) and inlet ports (2a, 4a) of adjacent oil hydraulic motors are connected to each other by main circuits (14, 15) to connect the oil hydraulic motors in series, an oil hydraulic pump (10) and a tank, respectively, are connected to the inlet port (6a) of the oil hydraulic motor located at one end and the outlet port (4b) of the oil hydraulic motor located at the other end via a main changeover valve (11), bypass passages (18, 21) are provided which connect the respective main circuits (15, 14) and motor-side circuits of the main changeover valve together, and at least one of changeover valves (17, 20) and throttles (19, 22), respectively, is provided in the respective bypass passages to provide communication and cutoff of the bypass passages.

Description

Description Drive device for crushing mixer

The present invention relates to a driving device of a crushing and mixing machine that crushes and mixes soil and soil with a soil improving material to form soil with improved soil. Background art

As a disintegrating mixer, there is known a disintegrating mixer in which a plurality of rotors are rotatably provided in a housing and each rotor is driven by a hydraulic motor.

In the drive device described above, each hydraulic motor is connected in series, and the hydraulic pressure discharged from one hydraulic pump is sequentially supplied to those hydraulic motors to drive each hydraulic motor. Each hydraulic motor can be driven even if the rotor load is different.

In other words, when the hydraulic pressure discharged from one hydraulic pump is separately supplied to multiple hydraulic motors and driven, the hydraulic pressure is supplied only to the hydraulic motor with the smallest load, and the other hydraulic motors are driven. Since it is not possible to do so, the discharge pressure oil of the hydraulic pump is supplied to the inlet port of the first hydraulic motor, and the outlet port of the first hydraulic motor is connected to the inlet port of the second hydraulic motor. The hydraulic motors are connected to a series, and these hydraulic motors are connected to a series, and even if the load of each hydraulic motor is different, each hydraulic motor is driven by the discharge hydraulic oil of one hydraulic pump. I am trying to do it. By the way, when each hydraulic motor is connected to the series as described above, the differential pressure between the inlet pressure and the outlet pressure of each hydraulic motor must be set to a pressure Pa that matches the required driving torque. The inlet pressure of the motor is Pa, the outlet pressure of the next hydraulic motor is Pa, the inlet pressure of that hydraulic motor is 2 x Pa, and the outlet pressure of the next hydraulic motor is 2 XP and the inlet pressure of the hydraulic motor is 3 x Pa. Therefore, the normally required maximum discharge pressure of the hydraulic pump is the value of (pressure Pa corresponding to the normally required drive torque) X (the number of hydraulic motors).

In addition, in the above-mentioned disintegrating mixer, the torque of the hydraulic motor when the rotor is driven in a steady state is small, but the torque of the hydraulic motor required when starting the rotor is large, so that the hydraulic pump is started. The maximum discharge pressure required at the time is (pressure corresponding to the torque required at startup) X

(The number of hydraulic motors). Therefore, the required horsepower of the driving source such as the engine is further increased.

This makes the drive expensive.

In view of the above problems, the present invention provides a drive device for a crushing and mixing machine in which the maximum discharge pressure of a hydraulic pump required at the time of startup is reduced as compared with the conventional case, so that the drive device is inexpensive. The purpose is to provide Disclosure of the invention

The driving device of the crushing and mixing machine according to the present invention comprises:

In a disintegration mixer in which a plurality of rotors are rotatably provided in a housing, and each of the rotors is driven by each hydraulic motor, The hydraulic motor is connected in series by connecting the outlet port and the inlet port of the adjacent hydraulic motor with the main circuit, and the inlet port of the hydraulic motor located at one end is connected to the other port. The hydraulic pump and the tank are connected via the main switching valve to the outlet port of the hydraulic motor located at the end, respectively.

A bypass path is provided to connect each of the main circuits and the motor side circuit of the main switching valve, and each of the bypasses is provided with at least one of a switching valve for communicating and blocking the bypass and at least one of the throttles. is there.

And in the above configuration,

The switching valve and the throttle may be provided in each of the bypasses.

In addition, each of the bypasses is provided with the switching valve and a pressure sensor for detecting the pressure of each of the bypass passages, and shuts off the switching valve of the corresponding bypass passage when the pressure detected by the pressure sensor reaches a predetermined pressure. It may be equipped with a controller for positioning.

Further, the throttle may be provided in each of the bypasses. According to the above configuration,

The hydraulic motor is connected in series by connecting the outlet port and the inlet port of the adjacent hydraulic motor with a main circuit, and the inlet port of the hydraulic motor located at one end is connected to the inlet port. The hydraulic pump and the tank are connected to the outlet port of the hydraulic motor located at the other end via the main switching valve 11, respectively.

A bypass path is provided for connecting each of the main circuits and the motor side circuit of the main switching valve, and each of the bypass paths is connected to each of the bypass paths. • Since at least one of the switching valve and the throttle to be shut off is provided respectively, after the switching valve is brought into the communicating state, by the action of the throttle, and by sequentially turning the switching valve into the shutting state, Or, by the action of the aperture only,

Since the start can be started sequentially from the hydraulic motor farthest from the hydraulic pump, the maximum discharge pressure of the hydraulic pump can be set to the starting pressure + the steady pressure X (the number of hydraulic motors-1). It will be cheaper. Also, since the starting pressure supplied to the hydraulic motor is smaller than when all hydraulic motors are started simultaneously, the hydraulic motor can be made smaller.

In addition, in the case where a switching valve for communicating / cutting off the bypass path is provided in each bypass path,

By setting the switching valve to the shut-off position when the engine is started and steady drive is started, the hydraulic oil discharged from the hydraulic pump flows sequentially through each hydraulic motor, so that each rotor does not malfunction. Can be driven reliably. BRIEF DESCRIPTION OF THE FIGURES

The invention will be better understood from the following detailed description and the accompanying drawings illustrating an embodiment of the invention. The embodiments shown in the accompanying drawings are not intended to specify the invention, but merely to facilitate explanation and understanding.

In the figure,

FIG. 1 is an explanatory diagram of a crushing and mixing machine including a first embodiment of a driving device according to the present invention. FIG. 2 is a hydraulic circuit diagram of the first embodiment of the present invention.

FIG. 3 is an explanatory diagram at the start of startup in the first embodiment. FIG. 4 is an explanatory diagram at the time of steady driving in the first embodiment. FIG. 5 is a hydraulic circuit according to a second embodiment of the present invention. FIG.

FIG. 6 is a hydraulic circuit diagram of a third embodiment of the present invention. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, a drive device of a crushing and mixing machine according to a preferred embodiment of the present invention will be described with reference to the accompanying drawings.

As shown in FIG. 1, the disintegration mixer includes a first rotor 3 rotated by a first hydraulic motor 2, a second rotor 5 rotated by a second hydraulic motor 4, and a third hydraulic motor 6 in a housing 1. A third rotor 7 is provided, which is rotated by a rotary shaft. Each rotor has a crushing mixer 8 radially attached to a rotating shaft. In this method, earth and sand and soil improvement material are introduced from the opening 9 of the nozzle 1 to disintegrate, mix, and stir to produce soil with improved soil quality.

Next, a description will be given of a first embodiment of the driving device for the crushing and mixing machine. As shown in FIG. 2, the discharge pressure oil of the hydraulic pump 10 is supplied and controlled to the first main circuit 12 and the auxiliary circuit 13 via the main switching valve 11. The first main circuit 12 is connected to the inlet port 6a of the third hydraulic motor 6, and the outlet port 6b is connected to the inlet port 2a of the first hydraulic motor 2 in the second main circuit 14. The outlet port 2 b is connected to the inlet port 4 a of the second hydraulic motor 4 in the third main circuit 15, and the outlet port 4 b is connected to the drain path 16.

The auxiliary circuit 13 is connected to a first bypass passage 18 by a first switching valve 17. Communication · It is cut off. The first bypass passage 18 is connected to the third main circuit 15 and has a throttle 19. Further, the auxiliary circuit 13 is communicated with the second bypass passage 21 by the second switching valve 20 and is shut off. The second bypass path 21 is connected to the second main circuit 14, and the throttle 22 is provided.

The main switching valve 11 is set to the shut-off position a by the panel force, and is set to the supply position b when the solenoid 11 a is energized. The first and second switching valves 17 and 20 are brought into the shut-off position c by spring force, and become the communication positions d when the solenoids 17 a and 20 a are energized, respectively. .

The second and third main circuits 14 and 15 are connected to a tank 25 via a suction valve 23 and a relief valve 24, respectively.

The first, second, and third hydraulic motors 2, 4, and 6 are configured such that the pressures (inlet pressures) of the inlet ports 2a, 4a, and 6a are equal to the pressures (outlet pressures) of the outlet ports 2b, 4b, and 6b. Start pressure in the direction of the arrow when the starting pressure is higher by P1 than the outlet pressure), and the differential pressure between the inlet pressure and the outlet pressure becomes steady pressure P2 (P1> P2) when in the steady driving state. It is becoming

In other words, when the hydraulic motor is started to drive, a high torque is required, so that the starting pressure P1 becomes high. In a steady driving state, the torque becomes small, so that the steady pressure P2 becomes low.

Next, the operation of the first embodiment will be described.

(At the start of startup)

As shown in FIG. 3, the solenoid 11a of the main switching valve 11 is energized to the supply position b, and the solenoids of the first and second switching valves 17 and 20 are turned on. Energize the nodes 17a and 20a, respectively, to set the communication position d.

Then, the discharge pressure oil of the hydraulic pump 10 is supplied to the inlet port 6a of the third hydraulic motor 6 in the first main circuit 12 and to the inlet port of the first hydraulic motor 4 in the first bypass passage 18. 4a to the outlet port 2b of the first hydraulic motor 2 and the second bypass path 21 to the inlet port 2a of the first hydraulic motor 2 and the outlet port 6b of the third hydraulic motor 6, respectively. Is performed.

As a result, the pressure (inlet pressure) at the inlet port 2a of the first hydraulic motor 2 and the pressure (outlet pressure) at the outlet port 2b become substantially equal. The pressure at 6a (inlet pressure) and the pressure at outlet port 6b (outlet pressure) are almost equal, and the pressure at inlet port 4a of the second hydraulic motor 4 (inlet pressure) and the outlet port 4b The pressure (outlet pressure) difference is the inlet pressure itself because the pressure at outlet port 4b is zero.

In the state described above, when the discharge pressure of the hydraulic pump 10 rises and the inlet pressure of the second hydraulic motor 4 becomes the starting pressure P1 at which the second hydraulic motor 4 generates a starting torque, the second hydraulic motor 4 starts. After that, the inlet pressure of the second hydraulic motor 4 becomes the steady pressure P2, but the pressure of the auxiliary circuit 13 is maintained at the starting pressure P i by the throttle 19 of the first bypass path 18. You.

As a result, the outlet pressure of the first hydraulic motor 2 becomes the steady pressure P2 and the inlet pressure becomes the starting pressure P1, so that the discharge pressure of the hydraulic pump 10 becomes the normal pressure P2 + the starting pressure P1. (1) When the pressure that generates the starting torque in the hydraulic motor 2 rises to P3, the differential pressure between the inlet pressure and the outlet pressure of the first hydraulic motor 2 becomes P3 (= P2 + Pl) — P2 = Pl. 1 hydraulic The motor 2 starts to start, and then the pressure of the first hydraulic motor 2 becomes twice the steady-state pressure P2, but the pressure of the auxiliary circuit 13 is maintained at the above-mentioned pressure P3 by the restriction 22 of the first bypass passage 21 Is done.

As a result, the inlet pressure of the third hydraulic motor 6 becomes P3 and the outlet pressure becomes (2 XP 2), so that the discharge pressure of the hydraulic pump 10 becomes the steady pressure (P2 X 2) + the starting pressure P 1 (3) When the pressure that generates torque at the start of the hydraulic motor 6 rises to P4, the pressure difference between the inlet pressure and the outlet pressure of the third hydraulic motor 6 becomes P4 (= P2 + P2 + P 1) — (P2 + P2) = P l, and the third hydraulic motor 6 starts to start.

As described above, the first, second, and third hydraulic motors 2, 4, and 6 need only have the pressure difference between the inlet pressure and the outlet pressure equal to the starting pressure P1 at which the starting torque is generated. Each hydraulic motor can be a small hydraulic motor, and the maximum discharge pressure of the hydraulic pump 10 is equal to the starting pressure P1 + the steady pressure (P2 X 2).

For example, if the starting pressure P 1 is 13 O kg / cm ² and the steady pressure P 2 is 30 kg / cm ² , the required maximum discharge pressure of the hydraulic pump 10 is 1 30 kg / cm ² ^{+ 3 0 kg / cm 2 x} 2) = 1 9 0 becomes kg / cm ^2.

On the other hand, when the first and second bypass passages 18 and 21 and the first and second switching valves 17 and 20 are not used, the maximum discharge pressure of the hydraulic pump 10 is 130 kg / cm ² x 3 = 390 kg / cm ² . (During steady drive)

As described above, when the first, second, and third hydraulic motors 2, 4, and 6 start to operate, as shown in FIG. 4, the solenoids 17 of the first and second switching valves 17 and 20 are used. a, 20a. 3, Connect the first and second hydraulic motors 6, 2, and 4 to the series.

In this way, the discharge pressure oil of the hydraulic pump 10 flows sequentially through the third hydraulic motor 6, the first hydraulic motor 2, and the second hydraulic motor 4, and flows through the first and second bypass passages 18, 21. Does not flow, so that each hydraulic motor can be reliably driven without malfunction.

Next, a second embodiment of the present invention will be described.

This is obtained by adding the following configuration to the configuration of the first embodiment except for the apertures 19 and 21.

That is, as shown in FIG. 5, the controller 30 controls the energization of the solenoids 11a and 20a of the first and second switching valves 17 and 20. 1, 1st, 2nd pressure sensors 31, 32 that detect the pressure in the second bypass passages 18, 21, and the start switch 3 connected to the controller 30 3 is provided.

When a start signal is input from the start switch 33, the controller 30 energizes the solenoids 17a and 20a of the first and second switching valves 17 and 20. The communication position d. When the first pressure sensor 31 detects the pressure P1, the power supply to the solenoid 17a is stopped, the first switching valve 17 is set to the shut-off position d, and the second pressure sensor 32 is set to the pressure P1. When P3 is detected, the power supply to the solenoid 20a is stopped, and the second switching valve 20 is set to the shut-off position d. Therefore, even if the second hydraulic motor 4 returns to the steady operation state, the pressure of the auxiliary circuit 13 is maintained at P 1, and even if the first hydraulic motor 2 returns to the steady operation state, the pressure of the auxiliary circuit 13 becomes P 3. Therefore, the second, first, and third hydraulic motors 4, 2, 6 are sequentially activated according to the same principle as the first embodiment, and the throttles 19, 22 are also activated. It becomes unnecessary.

Further, when the power to the solenoids 17a and 20a of the first and second switching valves 17 and 20 is stopped and the cutoff position c is reached, the third, first and second hydraulic motors 6, 2, and 4 are connected to the series.

Next, a third embodiment of the present invention will be described.

This configuration or et first of the first embodiment, the second switching valve 1 _7; are excluded from the 2 0.

That is, as shown in FIG. 6, the auxiliary circuit 13 is connected to the first and second bypass paths 18 and 21, and the first and second bypass paths 18 and 19 are respectively throttled 19 and 19. 22 is provided.

Therefore, the second, first, and third hydraulic motors 4, 2, and 6 are sequentially activated based on the same principle as in the first embodiment.

As described above, according to the present invention,

The hydraulic motors 6, 2, and 4 are connected in series by connecting the outlet port and the inlet port of the adjacent hydraulic motor with the main circuits 14 and 15, and located at one end. A hydraulic pump 10 and a tank are in contact with the hydraulic motor inlet port 6a and the hydraulic motor outlet port 4b located at the other end via the main switching valve 11 respectively.

Bypass paths 18 and 21 are provided for connecting the main circuits 15 and 14 with the motor side circuit of the main switching valve 11 respectively.The bypass paths 18 and 21 are provided in the respective bypass paths 18 and 21. Since at least one of the switching valves 17 and 20 and the throttles 19 and 22 are provided respectively, the switching valves 17 and 20 are connected to each other, and then the throttles 19 and 20 are connected. By the action of 22 or by sequentially closing the switching valves 17 and 20 or by the action of the throttles 19 and 22 only, Since starting can be started sequentially from the hydraulic motor 4 farthest from the hydraulic pump 10, the maximum discharge pressure of the hydraulic pump 10 can be set to the starting pressure + the steady pressure X (the number of hydraulic motors-1). And the driving device becomes inexpensive. Also, since the starting pressure supplied to the hydraulic motor is smaller than when all hydraulic motors are started simultaneously, the hydraulic motor can be downsized.

Also, when the bypass valves 18 and 21 are provided with switching valves 17 and 20 for connecting and disconnecting the bypass passages,

By setting the switching valve to the shut-off position when the drive is started and steady driving is performed, the discharge pressure oil of the hydraulic pump 10 flows through each hydraulic motor sequentially, so that malfunction does not occur. Each rotor can be driven reliably and reliably.

Although the present invention has been described with reference to illustrative embodiments, the disclosed embodiments do not depart from the spirit and scope of the present invention. Various modifications, omissions, and additions are possible. Is obvious to those skilled in the art. Therefore, the present invention should not be limited to the above-described embodiments, but should be understood to include the scope defined by the elements recited in the claims and their equivalents.

Claims

The scope of the claims

1. In a crushing and mixing machine in which a plurality of rotors are rotatably provided in a housing and each of the rotors is driven by a respective hydraulic motor,

The hydraulic motor is connected in series by connecting the outlet port and the inlet port of the adjacent hydraulic motor with the main circuit, and the inlet port and the other end of the hydraulic motor located at one end are connected. The hydraulic pump and the tank are connected via the main switching valve to the outlet port of the hydraulic motor located at

Crushing, wherein bypass paths are provided for connecting the respective main circuits and the motor-side circuit of the main switching valve, and at least one of a switching valve for communicating and blocking the bypass and at least one of the throttles is provided for each bypass; Drive for mixing machine.

2. The switching valve and the throttle are provided in each of the bypasses. The driving device of the crushing mixer according to claim 1.

3. Each of the bypasses is provided with the switching valve and a pressure sensor for detecting the pressure of each of the bypass passages, and when the pressure detected by the pressure sensor reaches a predetermined pressure, the switching valve of the corresponding bypass passage is shut off. The drive device for the crushing and mixing machine according to claim 1, further comprising a controller for positioning.

4. The drive device for the crushing and mixing machine according to claim 1, wherein the throttle is provided in each of the bypasses.