JPH0633222Y2 - Hydraulic circuit of hydraulic clutch - Google Patents

Description

TECHNICAL FIELD The present invention relates to a hydraulic circuit of a hydraulic clutch mainly used in a marine reduction / reversing machine.

2. Description of the Related Art In a hydraulic clutch provided in this type of marine reduction / reversing machine,
If a constant working oil pressure is supplied from the low speed region to the high speed region of the engine, an abnormal noise, so-called "rattle noise", is generated especially when the engine is running at low speed. It may occur due to backlash.

An example of the structure of a hydraulic circuit for preventing such "rattle noise" is described in Japanese Patent Publication No. 60-30582. In this system, the hydraulic oil pressure regulating valve of the clutch operating hydraulic circuit is capable of regulating the pressure in two stages: a high pressure state corresponding to the engine high speed rotation range and a low pressure state so as to prevent "rattle noise" during low speed rotation. ing.

Further, as a structure of a hydraulic circuit which can prevent the above-mentioned "rattle noise" other than the above-mentioned two-stage pressure regulating valve type, there is, for example, the one described in JP-A-58-166137. With this type, the amount of relief to the lubricating oil circuit or the drain side is changed by opening and closing the check valve in response to changes in the engine speed, and at low speeds the amount of relief is increased to maintain a low hydraulic pressure and to generate "noise". I try to prevent it.

Problems to be Solved by the Invention First, in the two-stage pressure regulating valve type as described in Japanese Patent Publication No. 60-30582, the engine speed is low as shown in FIG. 7, for example. While the operating oil pressure increases along the path of a → b → c → d as it increases from the rotation range, when the engine speed decreases from the high rotation range, the high working oil pressure d → e → f → b →
It will decrease along the route a. That is, in accordance with the increase / decrease in the engine speed, the operating oil pressure f → c → d → e →
A hysteresis phenomenon of f will appear, and depending on the situation, there may be a case where "rattle noise" occurs in the deceleration reverse rotation number and a case where it does not occur. On the other hand, the one disclosed in Japanese Patent Laid-Open No. 58-166137, which is not the two-stage pressure regulating valve type, has a low temperature even though the temperature regulating valve for preventing the influence of the temperature change of the hydraulic oil is provided. There are cases where the hydraulic pressure pattern changes depending on the time and when the temperature is high, and similarly, a "loud noise" is generated in the low engine speed region and may not be generated. Incidentally, in order to prevent such "rattle noise", it is sufficient to make the working oil pressure extremely low in the low engine speed region, but then there is a drawback that the hydraulic clutch will slip. Also,
In this type, an orifice is provided on the outflow side of the pressure regulating valve to leak a specific amount of hydraulic oil to the lubricating circuit. However, with such a simple orifice, it is necessary to shift the hydraulic oil pressure to the high pressure side. In some cases, the amount of leakage changes depending on the pressure of the hydraulic oil circuit, so there is a drawback that the hydraulic oil pressure increases slowly.

In view of such problems, the present invention can adjust the working hydraulic pressure to the hydraulic clutch to a low pressure state so as to prevent problems such as "rattle noise" even in the low engine speed range. Not only is it intended to provide a hydraulic circuit for a hydraulic clutch that prevents the hysteresis of the operating oil pressure that occurs due to an increase or decrease in the engine speed, and that does not change the hydraulic pressure pattern of the operating oil pressure even when the oil temperature changes. It was made as.

Means for Solving the Problems In order to achieve the above-mentioned object, the present invention provides a clutch operating hydraulic circuit from a hydraulic pump to a hydraulic clutch in which a constant amount of hydraulic oil leaks when the pump discharge pressure exceeds a certain level. It is characterized in that a flow rate adjusting valve with pressure compensation or a flow rate adjusting valve with temperature and pressure compensation is provided for holding the operation oil pressure at a predetermined high pressure to secure a predetermined high working hydraulic pressure.

Embodiment An embodiment of the present invention will be described below with reference to the drawings.
FIG. 1 is a hydraulic circuit diagram of a marine reduction / reversing machine according to the present invention. In the figure, (1) is the engine (2)
A hydraulic oil pump driven by a hydraulic oil pump (1), in which pressure oil discharged from the hydraulic oil pump (1) is connected to a discharge side of the hydraulic oil pump (1).
It is adapted to be supplied to one input port of the forward / reverse switching valve (5) via a known trolling device (4) installed in the middle of the. A forward clutch (6) and a reverse clutch (7) are connected to the two output ports of the forward / reverse switching valve (5). A branch circuit (8) branched from the clutch operating hydraulic circuit (3) is connected to the other input port of the forward / reverse switching valve (5) on the upstream side of the trolling device (4). Also,
Similarly, (9) shows a hydraulic oil pressure regulating circuit branched from the clutch hydraulic pressure circuit (3) on the upstream side of the trolling device (4).
A known hydraulic oil pressure regulating valve (10) with a loose fitting valve is installed.
It should be noted that this hydraulic oil pressure regulating valve (10) with a loose fitting valve has a back pressure circuit connected to the remaining output port of the forward-reverse switching valve (5).
(11) is connected. The drain port of the hydraulic oil pressure regulating valve with a loose fitting valve (10) has a lubricating oil circuit including an oil cooler (12) and a lubricating pressure regulating valve (13) in the middle portion thereof.
(14) is connected. The oil discharged from the lubricating pressure regulating valve (13) is supplied to each part as lubricating oil.

Further, (15) shows a hydraulic regulator according to the present invention, which includes a low pressure regulating valve (16) connected to the clutch operating hydraulic circuit (3) and the low pressure regulating valve. It has a basic configuration including a flow rate adjusting valve with pressure compensation (17) arranged on the downstream side of (16).

Next, a specific structure of the hydraulic pressure regulator (15) will be described. As shown in FIGS. 2 and 3, one end of the hydraulic pressure regulator (15) has an upper wall surface (18) of the body case (18).
A stepped valve disc insertion hole (19) is formed vertically to face a), and the main body of the pressure compensation flow control valve (17) is inserted into this stepped valve disc insertion hole (19). The constituent valve element (20) is slidably inserted. The valve body (20) includes a small piston portion (21) formed in a small diameter corresponding to the small diameter portion (19a) on the lower side of the stepped valve body insertion hole (19), and the small piston portion (21). twenty one)
The large piston part (22) formed on the upper side of the stepped valve body insertion hole (19) is formed on the upper side of the large piston part (22).
A flow control spring (24) is arranged between the case lid (23) attached to the main body case (18) so as to close the opening of the flow control spring (24). This flow control spring (2
The lower end side of 4) is in contact with the large piston portion (22) at the bottom surface of the upper oil chamber (25) in which the large piston portion (22) is recessed. That is, the valve body (20) is the flow control spring (24) described above.
Will always be urged downwards. This valve body
In (20), a vertical oil passage (26) along the longitudinal direction of the small piston portion (21) is formed, and the lower end portion of this oil passage (26) is formed in the small piston portion (21). It communicates with a lower oil chamber (27) formed facing the end face. Also, this oil passage (26)
The upper end of the is near the large piston part (22),
To the circumferential chamber (28) formed between the intermediate step portion of the stepped valve body insertion hole (19) and the large piston portion (22), the small piston portion (21)
They communicate with each other through lateral holes (29) (29) opened in the wall surface of the.
A vertically elongated annular groove (30) is formed in the upper and lower centers of the small piston part (21).
The annular groove (30) is also communicated with the oil passage (26) through the lateral holes (31) (31) formed in the small piston portion (21).

On the other hand, (32) shows a piston body with a guide which constitutes the pressure regulating valve (16) for low pressure, and this piston body with a guide (32) is also slidable vertically in the lower side of the body case (18). Has been inserted. When the guide portion (33) of the guided piston body (32) moves in the vertical direction, the small diameter portion (1) of the stepped valve body insertion hole (19) is
The communication area between the oil passage (34) communicating with 9a) and the pressure regulating valve chamber (35) formed in the upper portion of the piston body (32) is changed. Reference numeral (36) denotes a pressure adjusting spring whose one end contacts the piston body with guide (32). The lower wall surface (18b) of the body case (18) is attached with a support member (38) in which a low pressure adjusting screw (37) having a spring retainer portion (37a) at one end thereof is screwed into a penetrating state. The lower end side of the pressure adjusting spring (36) is in contact with the spring retainer portion (37a).

Further, in the main body case (18), as shown in FIG. 2, an oil passage (39) whose one end side faces the small diameter portion (19a) and opens.
Is formed so as to face the annular groove (30) of the small piston portion (21). The other end of the oil passage (39) is horizontally oriented and then bent at a substantially right angle to ascend, and the case lid (23) and the main body case (through the orifice (40) arranged in the middle of the oil passage (39). It communicates with the oil passage (41) provided between the oil passage (41). The oil passage (41) is arranged so as to face the upper oil chamber (25), and a branched oil passage (42) branched from the upper oil chamber (25) passes through the oil passage (43) of the main body case (18). To the connection port (44). A bypass circuit (45) leading to the lubricating oil circuit (14) is connected to the connection port (44) as shown in FIG. As shown in FIG. 2, a switching screw (46) for opening and closing the oil passage (39) is screwed in the main body case (18) so as to be able to move back and forth. ) Is closed, the oil passage (39) is closed by a bent portion as shown by a chain double-dashed line, so that the oil flow is blocked.

Next, explaining the function of this hydraulic regulator (15),
The pressure oil branched from the clutch operating hydraulic circuit (3) flows into the pressure regulating valve chamber (35) through the lateral hole (47) shown in FIG. 3, and then resists the urging force of the pressure regulating spring (36). And push down the piston body (32) with guide to flow out to the oil passage (34). The pressure oil flowing out to the oil passage (34) flows into the annular groove (30) provided in the valve body (20), and most of the pressure oil is directly in the oil passage (39).
After flowing out to, it is introduced into the oil passage (41) through the orifice (40). A part of the pressure oil that has flowed into the oil passage (41) is introduced into the upper oil chamber (25), while most of it is connected via the branch oil passage (42) and the oil passage (43). After being discharged to (44), it is supplied to the lubricating oil circuit (14) via the bypass circuit (45).

The remaining portion of the pressure oil that has flowed into the annular groove (30) through the oil passage (34) is the lateral holes (31) (31) of the small piston portion (21).
Is introduced into the oil passage (26) through the above, and a part thereof flows out to the lower oil chamber (27) facing the end face of the small piston portion (21), while the remaining part is the lateral hole (29) ( After passing through 29), it will flow out to the perimeter chamber (28).

That is, the valve body (20) includes the upward pressing force F ₁ generated by the pressure oil in the lower oil chamber (27) and the peripheral chamber (28), the pressure oil in the upper oil chamber (25) and the flow control spring (24). When the downward pressing force F _{2 due} to is balanced, it is stopped. In this case, the hydraulic pressure on the upstream side of the orifice (40) is set to P ₁ ,
While setting the hydraulic pressure on the downstream side to P ₂ , the effective pressure receiving area of the small piston portion (21) in the lower oil chamber (27) is A ₁ , and the upper oil chamber (25)
When the effective pressure receiving area of the large piston portion (22) at A is A ₂ , the following relational expression holds.

First, the upward pressing force F ₁ is F ₁ = P ₁ × A ₁ + P ₁ × (A ₂ −A ₁ ) = P ₁ × A ₂
………………… (1).

On the other hand, the downward pressing force F ₂ is represented by F ₂ = P ₂ × A ₂ + F ₃ (2) F ₃ is a flow control spring (24)
Shows the spring force of.

In this case, the upward pressing force F ₁ is the downward pressing force F
When it is larger than ₂ , the pressure compensation flow control valve (17) starts to operate.

In this case, when the pump discharge amount is low (the engine speed is low), the amount of oil passing through the orifice (40) is small, so P ₁ ≈P ₂ …………………… (3 ) Is obtained, and the relational expression of F ₁ <F ₂ …………………… (4) is obtained from the above equations (1) and (2), and the flow control spring ( The valve body (20) is pushed downward by the spring force F _{3 of} 24). When the valve body (20) moves downward as described above, the annular groove (30) provided in the valve body (20).
And the communication area with the oil passage (34) on the inlet side, which is the pressure oil supply side, increases.

Therefore, the hydraulic fluid in the clutch operating hydraulic circuit (3) is
It is discharged to the bypass circuit (45) through the low pressure pressure regulating valve (16) and the pressure compensating flow rate regulating valve (17), and the working hydraulic pressure becomes a low pressure state.

On the other hand, when the pump discharge amount is large (the engine speed is a polygon), the amount of oil passing through the orifice (40) is limited, so that the hydraulic pressure P ₁ on the upstream side of the orifice (40) increases. , F ₁ = F ₂ ………………………… (5) The valve body (20) will move so that
(34) and the annular groove (30) are in equilibrium just before they are closed, whereby the pressure of the clutch operating hydraulic circuit (3) is adjusted by the hydraulic oil pressure regulating valve (10) with a loose fitting valve. Become. The clutch operating hydraulic circuit (3)
Pressure will be automatically compensated.

FIG. 4 is a graph showing the relationship between the engine speed and the operating oil pressure when all the functions of the oil pressure regulator (15) are exhibited.

That is, in the low engine speed range, the working oil pressure is maintained at a constant low pressure state by the low pressure regulating valve (16). Therefore, the slip ratio of the forward clutch (6) or the reverse clutch (7) selected by the forward / reverse switching valve (5) is kept constant, and an excessive slip state is avoided. In the meantime, as described above, the flow control valve with pressure compensation (17) does not operate, and the lubricating oil is supplied from the orifice (14) to the lubricating oil circuit (14).

On the other hand, when the engine speed increases, the pressure compensating flow control valve (17) operates and only a certain amount of lubricating oil is supplied to the lubricating oil circuit (14), so the operating oil pressure rises sharply and becomes high. It will be in a hydraulic state.

It should be noted that, by an experiment incorporating this hydraulic pressure regulator (15), even when the engine speed drops from the high speed state, the working oil pressure will drop in the same hydraulic pattern as when it rises, and almost no hysteresis will occur. It was confirmed that there was no. Moreover, since the hydraulic pressure P _{2 that} is substantially equal to the lubricating hydraulic pressure of the lubricating oil circuit (14) acts on the large piston portion (22), the working hydraulic pressure and the lubricating hydraulic pressure due to the temperature change of the oil cancel each other out. It was also confirmed that the operating pressure of the clutch operating hydraulic circuit (3) was hardly affected by the temperature change.

From the above, it was found that the working oil pressure, particularly in the low engine speed region, can be maintained in a stable state at all times.

Next, FIG. 5 is a graph showing the relationship between the engine speed and the operating hydraulic pressure when the function of the low pressure regulating valve (16) in the hydraulic pressure regulator (15) is stopped.

In this case, like the hydraulic pattern shown in FIG.
In the engine low speed range, the operating oil pressure cannot be maintained at a low pressure in a constant state, but when the engine speed is low, the operating oil pressure can be in a low pressure state, and when the engine speed is high, it is in a high oil pressure state. It will be possible.

Furthermore, FIG. 6 is a graph showing the relationship between the engine speed and the working oil pressure when the oil passage (39) leading to the lubricating oil circuit (14) is cut off by using the switching screw (46). There is.

That is, in this case, the function of the hydraulic pressure regulator (15) is stopped, so that the hydraulic pressure of the clutch operating hydraulic circuit (3) rises rapidly to a high hydraulic pressure state. Therefore, there is an advantage that the forward clutch (6) to which such an operating oil pressure is supplied does not slip and the bottoming work can be easily performed at low speed.

The flow rate control spring shown in FIG. 2 and FIG.
If a shim or the like is interposed between the valve body (24) and the valve body (20), the spring force F ₃ acting on the valve body (20) of the flow compensating valve with pressure compensation (17) can be adjusted. it can.

Further, in this embodiment, the hydraulic pressure regulator (15) connected to the clutch operating hydraulic circuit (3) is provided with the pressure compensating flow rate regulating valve (17). A flow rate adjusting valve may be provided. Then, there is an advantage that the working oil pressure of the clutch working hydraulic circuit (3) is not further influenced by the oil temperature.

Effects of the Invention As described above, in this invention, the clutch operating hydraulic circuit from the hydraulic oil pump to the hydraulic clutch is provided with the pressure adjusting flow rate adjusting valve or the temperature pressure compensating flow rate adjusting valve. As described in JP-B-60-30852, it is possible to solve the problem of the hysteresis of the operating hydraulic pressure due to the adoption of the two-stage pressure regulating valve structure, and to completely prevent the "rattle noise" in the low engine speed range. It has become possible. Moreover, according to the present invention, unlike the one disclosed in Japanese Patent Laid-Open No. 58-166137, the influence of the temperature change of the oil temperature is removed without installing a special temperature control valve, and a constant hydraulic pressure pattern is always provided. It is possible to obtain the above, and it is possible to obtain the remarkable effect that the occurrence of “rattle noise” particularly in the low engine speed range can be eliminated without extremely lowering the working hydraulic pressure.
Further, when the discharge pressure exceeds a certain level, the flow rate control valve with pressure compensation leaks a certain amount of hydraulic oil to the lubricating oil circuit side, etc. regardless of the pressure of the circuit on the hydraulic oil pump discharge side, thereby increasing the hydraulic pressure. As described above, the hydraulic oil pressure is changed when the engine speed changes from low speed to high speed, like the one with a rattling noise prevention mechanism that keeps the operating oil pressure low when the engine discharges at low speed as described above. When it is necessary to shift the pressure to the high pressure side, the hydraulic oil pressure can be quickly raised, and such a mechanism can be realized without using the two-stage pressure regulating valve.

[Brief description of drawings]

FIG. 1 is a hydraulic circuit diagram of a marine reduction / reversing machine according to the present invention, and FIG. 2 is a partially cutaway sectional view showing a concrete structure of a hydraulic pressure regulator having a flow rate adjusting valve with pressure compensation. FIG. 4 is a cross-sectional view taken along the line AA in FIG. 2, FIG. 4 is a graph showing the relationship between engine speed and working hydraulic pressure when all the functions of the hydraulic pressure regulator are exhibited, and FIG. FIG. 6 is a graph showing the relationship between the engine speed and the operating oil pressure when the function of the low pressure regulator of the regulator is stopped, and FIG. 6 shows the engine speed and the engine speed when the function of the hydraulic regulator is stopped. FIG. 7 is a graph showing the relationship between the operating oil pressure and the relationship between the engine speed and the operating oil pressure, which shows the problem of the one disclosed in Japanese Patent Publication No. 60-30852 shown as a conventional example. (1) ... Hydraulic oil pump, (3) ... Clutch operating hydraulic circuit, (6) ... Forward clutch, (7) ... Reverse clutch, (15) ... Hydraulic regulator, (16) ... Low pressure regulating valve, (17) )… Flow control valve with pressure compensation.

Claims (1)

[Scope of utility model registration request] 1. A pressure compensator for maintaining a predetermined high working oil pressure in a clutch working hydraulic circuit from a working oil pump to a hydraulic clutch when the pump discharge pressure exceeds a certain value to keep a leak amount of the working oil constant. A hydraulic circuit for a hydraulic clutch, which is provided with a flow rate adjusting valve with temperature control or a flow rate adjusting valve with temperature and pressure compensation.