JPH04122294U - Hydraulic circuit for low hydraulic mooring machine - Google Patents

Abstract

(57) [Summary] [Purpose] The doubling speed characteristic of the mooring machine's reeling and unwinding is increased from about 3 times the previous speed to about 6 times. [Configuration] The pump part has two pumps: a high-pressure side pump and a low-pressure side pump.
The stands are arranged in parallel, the flow paths are communicated in parallel, and the respective discharge ports are connected via check valves. The low-pressure pump is equipped with an unload valve on the discharge side. When the pressure in the piping is high, the unload valve opens to bypass the discharged fluid from the low-pressure pump, and when the pressure is low, the unload valve opens. When the valve is closed, the fluid discharged from the low-pressure pump merges with the fluid discharged from the high-pressure pump and flows toward the motor, increasing the speed of the motor. Even though the fluid volume increases, the fluid pressure decreases, so the motor will not be overloaded.

Description

[Detailed explanation of the idea]

0001

[Industrial application field]

This invention relates to a mooring machine driven by low hydraulic pressure, and in particular, the mooring machine is driven by low hydraulic pressure. Low hydraulic pressure that can increase the winding and unwinding speed to about 6 times the rated load. This article relates to a hydraulic circuit for type mooring aircraft.

0002

[Conventional technology]

Conventionally, the hydraulic circuit diagram of a low-hydraulic mooring machine for berthing and unberthing ships was shown in Figure 8. There's something to see. Figure 8 is a diagram showing the hydraulic pressure state in the piping during the winding stroke. Ru. 101 is a pump section, 102 is a motor section, and 103 is a control section. Pump part 10 1 includes a pump 104, an electric motor 105 that drives the pump 104, and a pipe inside. A relief valve 106 that releases liquid when the pressure becomes high, and a relief valve 106 that responds to increases and decreases in the amount of liquid in the piping. A liquid tank 107 is provided for storing liquid. Inside the motor section 102 has three motors I', II', and III' mounted on the same axis, and this shaft drives the rope. It is connected to the drum 111 for winding and feeding. The control unit 103 has a slider that switches the mooring machine to three positions: retracting, neutral, and extending. There is a control valve 108 of a double type. In addition, the piping is arranged so that the liquid reaches the three motors I', II', and III' according to the load. a first distribution valve 109 that distributes liquid to the motor II' in response to the pressure within the motor II'; There is a second distribution valve 110 that distributes liquid to III'. The first distribution valve 109 is a pilot-driven two-way valve, and the second distribution valve 110 is a pilot-driven two-way valve. It is a pilot-driven three-way valve. The reason why the second distribution valve is a three-way valve is that when dispensing, the discharge side from motor III' , motors II' and I', it is necessary to use a three-way valve.

[0003] The first distribution valve 109 and the second distribution valve 110 are designed such that the pressure receiving area of the pilot piping is different (see FIG. 11(B)) so as not to cause chattering of the valves during switching. ), or using special valves as shown in Figures 9-11. Figure 9 (A) is a cross-sectional view of the special valve. In the case of the first distribution valve, passages a and b are closed if the pressure inside the pipe is 20 kg/cm ² or less, and open if it is 20 kg/cm ² or more. It is set as follows. Since there is a small hole e at the bottom of the valve C, the valve is closed by the force of the spring s. The force trying to open the valve C is the product of the area and pressure corresponding to P in Fig. 11(A), and the force trying to close the valve is the product of the area and pressure corresponding to Y, the spring force f, and is the sum of When the pressure inside the pipe increases to 20 kg/cm ² or more, the valve is pushed upward. When the valve moves slightly upward, the liquid path g opens as shown in Figure 9 (B), and pressure also acts on the area corresponding to the area Q in Figure 11 (A), trying to open the valve. Force increases as the product of (P+Q) and pressure. h serves as a liquid escape path and is connected to a drain pipe or an unpressurized liquid. FIG. 10(A) is a diagram showing the state when the switch is made. Once switched, the difference in area becomes large, and the force pushing it open becomes larger than when it is closed. In other words, even if the pressure becomes low, the valve C can continue to open because the pushing force is large. Therefore, chattering does not occur during switching. The pressure becomes even lower (close to zero) and the closing force (spring force f) increases, causing the valve C to close. Incidentally, during pilot driving, the same effect as described above can be obtained by making the pressure receiving area of the pilot pressure different as shown in FIG. 11(B). Note that FIG. 10(B) is a cross-sectional view of the casing portion d of the valve body, and FIG. 11(A) is a cross-sectional view of the valve C. In this way, chattering is prevented when switching the distribution valve.

0004 In the above configuration, when the control valve 108 is in the retracting position as shown in FIG. The liquid from the pipe 104 flows through the motor I', the first distribution valve 109, and the second distribution valve as shown by the arrow. It flows to 110. If the entrainment load is small and the pressure in the piping is small, the liquid will flow to the motor I' However, when the load becomes large and the pressure inside the piping increases, the first distribution valve 109 is opened, and the liquid also flows to motor II. Furthermore, the load increases and the inside of the piping When the pressure increases, the second distribution valve 110 also opens, and the liquid also flows to the motor III. In this way, the pressure inside the pipe is sensed according to the load, and the first distribution valve 109 and the second distribution valve 110 in sequence, start motors II' and III' in sequence, and reduce the reeling speed. This allows it to handle large loads. With the above configuration, low negative The maximum speed characteristic during loading was about 3 times. However, there is also a desire to increase the winding speed for low loads, especially for ships. When leaving the berth, if the ship's line is disconnected by a bit on the quay, the ship must quickly reel it in. , there is a risk of getting wrapped around the propeller, and a speed of about 40 to 50 meters/minute is required. Recently, speeds of 60 meters/minute or more are sometimes required.

[0005]

[Problem that the idea aims to solve]

According to the hydraulic circuit of the conventional mooring machine mentioned above, in order to triple the speed characteristics or more, the rated By increasing the speed under load and satisfying the required speed under low load, the required horsepower was also reduced. There was a problem that the horsepower became larger than a predetermined amount. Therefore, the purpose of this invention is to Hydraulic pressure for mooring aircraft that allows you to obtain double speed characteristics of any size without changing the horsepower of The purpose is to provide circuits.

[0006]

[Means to solve the problem]

In order to solve the above problems, the present invention consists of a pump section, a motor section, and a control section. In a mooring machine, a high pressure side pump and a low pressure side pump are arranged in parallel in the pump section, Connect the liquid lines in parallel and install an unload valve on the discharge side of the low-pressure pump to When the pressure is high, open the unload valve to bypass the discharge fluid from the low pressure side pump. When the pressure in the liquid pipe is low, the unload valve closes and the low pressure side pump is turned off. Low hydraulic pressure configured so that the discharge liquid enters the liquid pipe and increases the speed of the mooring machine An object of the present invention is to provide a hydraulic internal circuit for a type mooring machine.

[0007]

[Effect]

According to the low hydraulic pressure circuit for mooring machines of this invention, the load is large and the pressure inside the piping is high. When the unload valve opens, the liquid from the low-pressure pump is bypassed, and the high-pressure Only liquid from the side pump goes into the piping. When the load decreases, the pressure inside the pipe increases. As the pressure decreases, the unload valve closes, and the liquid from the low-pressure side pump also flows into the piping. The speed becomes faster. Even if the fluid volume increases, the fluid pressure remains low, so the motor will not be overloaded. stomach.

[0008]

【Example】

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a hydraulic circuit for a low hydraulic mooring machine according to the present invention, and shows the state when the control valve is in the retracting position. 1 is a pump section, 2 is a motor section, and 3 is a control section. Inside the pump section 1 are a high-pressure side pump 4, an electric motor 5 that rotates the high-pressure side pump 4, a relief valve 6 that releases liquid when the inside of the piping becomes high pressure, and a relief valve 6 that responds to increases and decreases in the amount of liquid inside the piping. A liquid tank 7 for storing liquid is located in a part of the piping. Although the above configuration is the same as the conventional example, in the present invention, a low pressure side pump 12 is further mounted coaxially with the high pressure side pump 4. Further, an unload valve 13 is installed on the low-pressure discharge side. The outlet side of the unload valve 13 is connected to the suction sides of the high pressure side pump 4 and the low pressure side pump 12. As shown in the figure, the unload valve 13 is a pilot-driven two-way valve that opens and closes by sensing the pressure inside the liquid pipe. This unload valve 13 is equipped with a chattering prevention device (FIGS. 9 to 11) during switching, as described in the prior art section. It is set to open when the pressure inside the pipe reaches 22 kg/cm ² . The relief valve 6 is set to open when the liquid pressure in the pipe reaches 45 kg/cm ² . Check valves are installed on the discharge sides of the high-pressure side pump 4 and the low-pressure side pump 12, respectively, as shown in the figure.

[0009] Reference numeral 2 denotes a motor section, and three motors I, II, and III of equal capacity are mounted coaxially, and this shaft is connected to a drum 11 for reeling in and letting out the mooring machine. Reference numeral 3 denotes a control section, which includes a sliding control valve 8 that switches between three positions: internal winding, neutral, and feeding, and a first distribution valve 9 that controls the liquid to flow into the motor II according to the load. There is a second distribution valve 10 which controls the flow into motor III. The first distribution valve 9 is pilot-driven and opens when the pressure inside the pipe reaches 20 kg/cm ² .The second distribution valve 10 is also pilot-driven and is set to open when the pressure inside the pipe reaches 33 kg/cm ² . ing. Both the first distribution valve 9 and the second distribution valve 10 are equipped with the above-mentioned chattering prevention device (FIGS. 9 to 11) to prevent chattering during switching. Figure 1 shows a case where the load is small and the pressure inside the pipe is 20 kg/cm ² , and high pressure is acting on the part of the pipe indicated by the thick line. That is, since the unload valve 13 of the low-pressure side pump 12 is in a closed state, the liquid on the discharge side of the low-pressure side pump 12 enters the discharge side of the high-pressure side pump 4. Therefore, since the amount of liquid becomes large, the motor I rotates at high speed. In the case of the conventional technique shown in FIG. 8, the double speed characteristic is about 3 times when the load is low, but in the case of FIG. 1, the double speed characteristic can be made about 6 times. In order to rotate the motors II and III together with the motor I, as shown in FIG. 1, the liquid exiting the motor I flows to the inlet side of the motors II and III as shown by the arrow.

[0010] FIG. 2 shows a state in which the pressure inside the pipe reaches 20 kg/cm ² or more, and the first distribution valve 9 is opened, so that the liquid flows to both motors I and II. Since the liquid from the low-pressure side pump 12 flows into the pipe together with the liquid from the high-pressure side pump 4, the drum 11 rotates at high speed. Since the motor III rotates together with the motors I and II, the return water from the motors I and II flows through the second distribution valve 10 to the inlet side of the motor III, as shown in FIG.

[0011] Figure 3 shows when the load becomes large and the pressure inside the pipe reaches 20 kg/ ^cm2 , and the unload valve 13 is activated and opened, so that all the liquid discharged from the low pressure side pump 12 is bypassed. However, only the liquid discharged from the high pressure side pump 4 flows without entering the pipe. This is because the pressure inside the piping is high, so if the amount of liquid is large, the electric motor 5 will tend to be overloaded.

FIG. 4 shows a situation where the load becomes even higher and the pressure inside the pipe exceeds 33 kg/cm ² , and the second distribution valve 10 opens, allowing liquid to flow to the motor III. All three motors I, II, and III operate. The liquids on the outlet sides of the motors I, II, and III join together midway as shown in FIG. 4 and return to the pump 1. In this case as well, since only the amount of liquid from the high-pressure side pump 4 is flowing, overloading of the electric motor 5 is prevented.

[0013] FIG. 5 shows the control valve 8 in the neutral position. As shown in Fig. 5, the liquid discharged from the high pressure side pump 4 and the low pressure side pump 12 is Return to part 1. One part of the liquid also tries to flow to the motor part 2 as shown by the arrow, but the motor III is in a loop shape, and the same pressure acts on both sides of the entrance and exit of motors I and II. Since the first distribution valve 9 is closed and there is a check valve in the control section 3, the liquid that enters is not circulated. Since the path is closed, motors I, II, and III do not rotate. Maintain rated load When the first distribution valve 9 and the second distribution valve 10 are switched, the motors I, II, and III are All circuits are closed by check valves in the control section 3, so the motor does not rotate.

FIG. 6 shows the control valve 8 in the delivery position, when the pressure inside the pipe is 22 kg/cm ² or less, the unload valve 13 is closed, and the liquid discharged from the low-pressure side pump 12 is also in the pipe. Indicates when it is flowing. The liquid goes to the outlet side of motor III 3 and rotates motor III. During feeding, the load is small, so only motor III needs to be rotated. In order to rotate the motors I and II, the liquid discharged from the motor III goes to the outlet side of the motors I and II, causing the motors I and II to rotate together with the motor III. When the pressure inside the pipe is 22 kg/cm ² or more, the unload valve 13 is opened, and the liquid from the low-pressure side pump 12 is completely bypassed and does not enter the pipe, and only the liquid from the high-pressure side pump 4 flows. . Therefore, the feeding speed becomes slow.

The low hydraulic pressure hydraulic circuit for mooring of the present invention has been described above as a circuit. Next, the performance of a mooring machine implementing the circuit of the present invention will be explained with reference to FIG. In Figure 7, the upper diagram is a diagram showing the relationship between load and pressure, with load % on the X axis and pump discharge pressure kg/cm ² on the Y axis, showing the hydraulic pressure according to the load %. It is. As mentioned above, the operating pressure of the first distribution valve is 20 kg/cm ² , so when the pressure is below 20 kg/cm ² , only the motor I is operating. Since the unload valve is still closed, the amount of liquid in the pipe is the total amount of liquid since both the high pressure side and low pressure side liquid enters. When the load increases to about 12%, the pressure increases to 20 kg/cm ² or more, the first distribution valve opens, and the motor II starts operating. Then, the discharge pressure drops instantaneously. However, since the first distribution valve 9 is equipped with a chattering prevention device (FIGS. 9 to 11) as described above, the first distribution valve remains open. Therefore, motors I and II are operating. When the load increases further to around 32%, the pressure rises to over 22 kg/ ^cm2 , the unload valve opens, and the liquid from the low-pressure pump is bypassed, so the liquid level in the piping is reduced to half the liquid level. becomes. When the load increases further to about 52%, the pressure increases to 33 kg/cm ² or more, the second distribution valve also opens, and motor III also operates. And the pressure drops instantly. However, since the second distribution valve is equipped with a chattering prevention device (FIGS. 9-11), the second distribution valve remains open. Therefore, three motors, I, II, and III, operate. When the load is 100%, the pressure will also be 40 kg/cm ² . That is, winding is normally performed at a normal pressure of around 40 kg/cm ² at 100% load.

The lower diagram in FIG. 7 is a diagram showing the relationship between load and speed, in which the X-axis shows load %, and the Y-axis shows speed (meters/minute) and speed (%). As explained in the case of the upper figure, when the load is less than 12%, the total amount of liquid in the pipe is reached (the flow rates of the high-pressure side pump and the low-pressure side pump are combined), and therefore the entrainment speed is also fast, reaching 45 meters. /quantile (600%). When the pressure exceeds 20 kg/cm ² and the first distribution valve opens, the liquid goes to both motors I and II, so the speed momentarily slows down to 24 m/min (320 m/min). %)become. As the load increases, the speed gradually decreases, and when the load reaches 32%, the unload valve opens and the liquid from the low-pressure side pump is bypassed, so the speed momentarily slows down to 10 m/min. Become. From this point on, the liquid amount becomes half the liquid amount (only the flow rate from the high pressure side pump). When the load increases further to 52%, the second distribution valve opens and the liquid flows to motor III, which also operates, so the speed momentarily slows down to 7.5 meters/min. That is, when the load is between 52% and 100%, three motors are operated, and the pressure inside the pipe is 33 to 40 kg/cm ² in a general usage condition, and the winding speed at this time is 7.5 meters/cm 2. As mentioned above, when the load is low and 12% or less, the winding speed is 45 meters/minute, and the double speed characteristic is 6. A diagram corresponding to the above explanation is described below the Y axis. The present invention is not limited to the above-mentioned embodiments, but can be implemented in any appropriate manner by making appropriate design changes.

[0017]

[Effect of the idea]

As explained above, according to the present invention, the low pressure side pump 12 and the unload valve 13 By adding this to the conventional equipment, when the pressure in the piping is low during low load, The liquid from the pressure side pump 12 enters the piping, so the amount of liquid increases and the speed at low loads is lower than before. It can be done quickly. Even if the liquid amount increases, the liquid pressure is low, so the electric motor 5 will not be overloaded. therefore Conventionally, with this type of equipment, the double speed characteristic at low loads was about 3 times, but it has been increased to about 6 times. It can be raised up to.

[Brief explanation of drawings]

[Figure 1] This is a circuit diagram of the hydraulic circuit for a low hydraulic mooring machine of the present invention when the load is small and the pressure inside the piping is 20 kg/kg.
cm ² or less and only one motor is operating.

[Fig. 2] In Fig. 1, the load increases and the pressure inside the pipe becomes 20 kg/cm ² or more, and the first distribution valve opens;
This shows when two motors are operating.

[Fig. 3] In Fig. 2, the load increases further and the pressure inside the pipe increases to over 22 kg/ ^cm2 , and the unload valve opens, bypassing the low-pressure side pump and turning on only the high-pressure side pump. This shows when the amount of liquid is entering the pipe (half the amount of liquid).

[Fig. 4] In Fig. 3, the load increases further and the pressure inside the pipe reaches 33 kg/ ^cm2 , the second distribution valve is opened and three motors are operating. There is. The liquid volume is half liquid.

[Fig. 5] In the hydraulic circuit for a low hydraulic mooring machine of the present invention,
The pressure state of the circuit is shown when the control valve is in the neutral position.

[Fig. 6] In the hydraulic circuit for a low hydraulic mooring machine of the present invention,
The pressure state of the circuit is shown when the control valve is in the extended position.

FIG. 7 is a diagram showing the performance of a mooring machine using the low hydraulic pressure circuit for a mooring machine of the present invention.

FIG. 8 is a diagram showing a hydraulic circuit for a conventional low hydraulic mooring machine.

[Fig. 9] (A) is a cross-sectional view showing the structure of a conventional special valve that serves as a distribution valve, and in this case, the distribution valve is closed, and (B) is a cross-sectional view showing the pressure inside the pipe in (A). FIG. 3 is a diagram showing a state where the distribution valve has started to open as the amount of the distribution valve increases.

[Fig. 10] (A) is a diagram showing a situation in Fig. 9 (B) where the pressure inside the pipe has further increased and the distribution valve is opened; FIG. 2 is a sectional view of a casing d of a conventional special valve.

FIG. 11(A) is a sectional view of a conventional special valve C serving as a distribution valve, and FIG. 11(B) is a diagram showing the structure of the conventional distribution valve when driven by a pilot. The dashed line indicates the pilot piping.

[Explanation of symbols]

1,101 Pump part 2, 102 Motor section 3,103 Control section 4,104 High pressure side pump 5,105 Electric motor 6,106 Relief valve 7,107 Oil tank 8,108 Control valve 9,109 First distribution valve 10, 110 Second distribution valve 11, 111 drum 12 Low pressure side pump 13 Unload valve a, b aisle c valve d Casing e small hole f Spring force G Liquid path h Liquid escape route s spring

Claims (1)

[Scope of utility model registration request] Claim 1: A mooring machine consisting of a pump section (1), a motor section (2), and a control section (3), in which a high pressure side pump (4) and a low pressure side pump (12) are connected in parallel within the pump section (1). An unload valve (13) is installed on the discharge side of the low-pressure side pump (4) to open the unload valve (13) when the pressure inside the liquid pipe is high. When the pressure inside the liquid pipe is low, the unload valve (13) is closed and the liquid discharged from the low pressure side pump (12) enters the liquid pipe, allowing the liquid discharged from the low pressure side pump (12) to bypass the vessel. Hydraulic circuit for low hydraulic mooring aircraft configured to increase aircraft speed.