CN107208624B - hydraulic device, internal combustion engine and ship - Google Patents
hydraulic device, internal combustion engine and ship Download PDFInfo
- Publication number
- CN107208624B CN107208624B CN201580073785.8A CN201580073785A CN107208624B CN 107208624 B CN107208624 B CN 107208624B CN 201580073785 A CN201580073785 A CN 201580073785A CN 107208624 B CN107208624 B CN 107208624B
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- China
- Prior art keywords
- auxiliary pump
- internal combustion
- combustion engine
- auxiliary
- hydraulic device
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/02—Stopping, starting, unloading or idling control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2207/00—External parameters
- F04B2207/01—Load in general
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/11—Kind or type liquid, i.e. incompressible
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Power Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Fluid-Pressure Circuits (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
Abstract
A kind of hydraulic device, the hydraulic device use the high-efficient region of auxiliary pump, and have: more auxiliary pumps (41), the more auxiliary pumps carry out pressure accumulation movement by the power of internal combustion engine (18)；Hydraulic-driven portion (54), the hydraulic-driven portion by the hydraulic of auxiliary pump (41) pressure accumulation by being driven；And clutch (44), the clutch is according to the load conditions of internal combustion engine (18), to reduce the operating number of auxiliary pump (41) in the case where lower than defined load, and the mode for the operating number for increasing auxiliary pump (41) in the case where higher than defined load makes auxiliary pump (41) stopping or operating.
Description
Technical field
The present invention relates in the driving of internal combustion engine by by multiple auxiliary pump pressure accumulations it is hydraulic come drive such as petrolift,
A kind of hydraulic device, internal combustion engine and the ship in hydraulic-driven portion as the actuator of exhaust valve driving.
Background technique
In the marine diesel engine as internal combustion engine, especially electronic-controlled engine, as hydraulic-driven portion
Petrolift and the lower part driving valve device (actuator) of exhaust valve driving pass through the hydraulic of the working oil by auxiliary pump pressure accumulation
It is controlled with solenoid valve.Such marine diesel engine has more to improve the redundancy in the damage of auxiliary pump
Platform auxiliary pump (for example, referring to patent document 1).
Existing technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 10-331772 bulletin
Problems to be solved by the invention
It is remaining auxiliary in order to be utilized the damage of the auxiliary pump of a part in the case where having more auxiliary pumps
Help pump to carry out the navigation of ship, discharge rate when each auxiliary pump is designed to make the actual motion of each auxiliary pump relative to
Maximum throughput has sufficient surplus.For example, being designed as the 30%~60% of maximum throughput.
Here, fuel injection amount reduces if the load reduction of marine diesel engine, therefore the necessary amount of working oil
It reduces.Also, in ship in recent years, have the tendency that carrying out low steaming to inhibit fuel consumption, thus practical fortune
The discharge rate of each auxiliary pump in row state tails off.For example, being designed as the 15%~30% of maximum throughput.
On the other hand, it is however generally that, if the discharge rate of each auxiliary pump becomes smaller, have the tendency that efficiency of pump reduction.Cause
This, in the marine diesel engine of present electronic control type, engine loading more it is low then using auxiliary pump efficiency more
Low region, the energy efficiency as engine and ship entirety are low.
Summary of the invention
The present invention is the invention for solving the above subject, and its purpose is to provide can not be influenced by engine loading
And use a kind of hydraulic device, combustion engine and the ship in the high-efficient region of auxiliary pump.
The method used for solving the problem
In order to achieve the above objectives, the characteristics of hydraulic device of the invention, is have: more auxiliary pumps, this more auxiliary
Pump is helped to carry out pressure accumulation movement by the power of internal combustion engine；Hydraulic-driven portion, the hydraulic-driven portion pass through by each auxiliary pump
The hydraulic of pressure accumulation drives；And auxiliary pump switching mechanism, the auxiliary pump switching mechanism according to the load condition of the internal combustion engine,
To reduce the operating number of the auxiliary pump in the case where lower than defined load, and in the case where higher than defined load
The mode for increasing the operating number of the auxiliary pump makes the auxiliary pump stop or operate.
It is assisted in the case where the load condition of internal combustion engine is lower than defined load by reducing according to the hydraulic device
The operating number of pump can be operated in each auxiliary pump with the high state of the efficiency of pump.On the other hand, in the load shape of internal combustion engine
It, can be in each auxiliary pump with the efficiency of pump by increasing the operating number of auxiliary pump in the case that state is higher than defined load
High state operating.It is used as a result, it is possible to not influenced by engine loading using the high-efficient range of auxiliary pump.
Also, in hydraulic device of the invention, it is characterized in that, the auxiliary pump switching mechanism is made of clutch,
The clutch is set between the transfer route that the power of the internal combustion engine is transmitted to the auxiliary pump, and the clutch
Device is not making the internal combustion engine stop to connect or cutting off the power of the internal combustion engine transmitted to the auxiliary pump.
According to the hydraulic device, not making internal combustion engine stop to connect or cutting off the internal combustion engine transmitted to auxiliary pump
Power, thereby, it is possible to the stopping or operating of auxiliary pump are carried out in the operation of internal combustion engine.
Also, in hydraulic device of the invention, it is characterized in that, it is also equipped with control unit, which obtains in described
The load of combustion engine, and controlled in a manner of the operating number to become the preset auxiliary pump according to the load described auxiliary
Help pump switching mechanism.
According to the hydraulic device, the operating number of auxiliary pump is automatically controlled by control unit, therefore can be obtained significantly
To the effect for not influenced and being used the high-efficient region of auxiliary pump by engine loading.
Also, in hydraulic device of the invention, it is characterized in that, it is also equipped with control unit, which obtains in operating
The auxiliary pump total discharge rate, and with according to total discharge rate and become the preset auxiliary pump operating number
Mode control the auxiliary pump switching mechanism.
According to the hydraulic device, the operating number of auxiliary pump is automatically controlled by control unit, therefore can be obtained significantly
To the effect for not influenced and being used the high-efficient region of auxiliary pump by engine loading.
Also, in hydraulic device of the invention, it is characterized in that, the auxiliary pump is the discharge rate that can make working solution
Variable variable displacement pump, the control unit make to stop in the case where reducing the operating number of the auxiliary pump
The discharge rate of the auxiliary pump gradually decrease, and after gradually increasing the discharge rate of the auxiliary pump of operating, control institute
State auxiliary pump switching mechanism.
The pressure of working oil can be prevented in the case where reducing the operating number of auxiliary pump according to the hydraulic device
Variation, the torque of auxiliary pump change and carry out the switching of auxiliary pump.
Also, in hydraulic device of the invention, it is characterized in that, the auxiliary pump is the discharge rate that can make working solution
Variable variable displacement pump, the control unit is in the case where making the increased situation of operating number of the auxiliary pump, in control auxiliary pump
After switching mechanism, the discharge rate of the auxiliary pump newly operated is gradually increased, and makes the row of the auxiliary pump in operating
Output gradually decreases.
The pressure of working oil can be prevented in the increased situation of operating number for making auxiliary pump according to the hydraulic device
Variation, the torque of auxiliary pump change and carry out the switching of auxiliary pump.
Also, in hydraulic device of the invention, it is characterized in that, the control unit is in the operating platform for making the auxiliary pump
In the case that number is reduced, the auxiliary pump different by the auxiliary pump made from upper one time stops controlling described in a manner of stopping
Auxiliary pump switching mechanism.
According to the hydraulic device, the total run time of each auxiliary pump can be made to homogenize and the damage for reducing auxiliary pump is general
Rate.
Also, in hydraulic device of the invention, it is characterized in that, the control unit obtains the discharge of each auxiliary pump
The gross pressure of working solution afterwards, and in the case where the preset pressure of the overall pressure ratio is low, so that the auxiliary stopped
The mode of pump operating controls the auxiliary pump switching mechanism.
According to the hydraulic device, in the case that auxiliary pump in operation breaks down, automatically backup can be used simultaneously
Obtain the working oil of necessary amount.
Also, in hydraulic device of the invention, it is characterized in that, the control unit is utilizing the auxiliary pump switching machine
Structure come make the auxiliary pump stop or operating in the case where by the state maintain as defined in the time.
For example, in navigation in bad weather, when screw rod exposes from the water surface, the load condition wink of internal combustion engine
When change.The variation of load condition relative to internal combustion engine instantaneous in this way, the operating or stopping for carrying out auxiliary pump have and make to bear
Carry the worry for changing and deteriorating.According to the hydraulic device, stop auxiliary pump by auxiliary pump switching mechanism or the feelings of operating
Under condition, by the way that the state is maintained the stipulated time, it is able to suppress the deterioration of load change.
Also, the characteristics of internal combustion engine of the invention, is have any one of the above hydraulic device.
According to the internal combustion engine, in hydraulic device, in the case where the load condition of internal combustion engine is lower than defined load, lead to
The operating number for reducing auxiliary pump is crossed, can be operated in each auxiliary pump with the high state of the efficiency of pump.On the other hand, in internal combustion
It, can be in each auxiliary pump by increasing the operating number of auxiliary pump in the case that the load condition of machine is higher than defined load
In with the efficiency of pump it is high state operating.As a result, it is possible to not influenced and used the high-efficient area of auxiliary pump by engine loading
Domain, and can be improved the energy efficiency as internal combustion engine.
Also, the characteristics of ship of the invention, is have above-mentioned internal combustion engine.
According to the ship, in hydraulic device, in the case where the load condition of internal combustion engine is lower than defined load, pass through
The operating number of auxiliary pump is reduced, can be operated in each auxiliary pump with the high state of the efficiency of pump.On the other hand, in internal combustion engine
Load condition than it is defined load it is high in the case where, by increase auxiliary pump operating number, can be in each auxiliary pump
With the high state operating of the efficiency of pump.As a result, it is possible to not influenced and used the high-efficient region of auxiliary pump by engine loading,
And it can be improved the energy efficiency as internal combustion engine and ship entirety.
Invention effect
In accordance with the invention it is possible to not influenced and used the high-efficient region of auxiliary pump by engine loading.
Detailed description of the invention
Fig. 1 is the outline side view using the ship of hydraulic device involved in present embodiment of the invention.
Fig. 2 is the skeleton diagram of hydraulic device involved in embodiments of the present invention.
Fig. 3 is the skeleton diagram of the auxiliary pump switching mechanism in hydraulic device involved in embodiments of the present invention.
Fig. 4 is the skeleton diagram of the auxiliary pump switching mechanism in hydraulic device involved in embodiments of the present invention.
Fig. 5 is the curve graph of the relationship of the engine load and working oil necessary amount that indicate that crank axle often rotates a circle.
Fig. 6 is the curve graph for indicating the relationship of engine load and crankshaft-rotation.
Fig. 7 is the curve graph for indicating the relationship of engine load and working oil necessary amount per unit time.
Fig. 8 is the curve graph for indicating the relationship of auxiliary pump delivery and the efficiency of pump.
Fig. 9 indicates the curve of engine load and working oil necessary amount and the relationship of auxiliary pump number of units per unit time
Figure.
Figure 10 is the flow chart for indicating the movement of hydraulic device involved in embodiments of the present invention.
Figure 11 is the flow chart for indicating the movement of hydraulic device involved in embodiments of the present invention.
Specific embodiment
Hereinafter, embodiment according to the present invention is described in detail based on attached drawing.In addition, the invention is not by this
Embodiment limits.Also, can and displacement be easy containing those skilled in the art in the structural element of following embodiments
Interior perhaps substantially the same content.
Fig. 1 is the outline side view using the ship of hydraulic device involved in present embodiment.
The ship of present embodiment has hull 10.The hull 10 has fore 11, stern 12, hull bottom 13 and shipboard
14.The water line (full load) of WL expression hull 10.On the quarter 12 sides by next door 16 divide organic cabin 17 to hull 10.And
And in cabin room 17 configured with the internal combustion engine (diesel engine) 18 as sustainer.Internal combustion engine 18 and transmitting propulsive force
Propeller 19 links.Also, hull 10 on the quarter 12 is provided with the rudder for controlling the direction of hull 10.The rudder main body 20 of rudder is supported
It is rotatable relative to hull 10.In the present embodiment, rudder main body 20 is installed on rotary shaft 21, which is installed to be
It is rotatable relative to hull 10.Also, rotary shaft 21 and driving machine (for example, drive device for hydraulic) 22 link.
Fig. 2 is the skeleton diagram of hydraulic device involved in present embodiment.Fig. 3 and Fig. 4 is involved by present embodiment
Hydraulic device in auxiliary pump switching mechanism skeleton diagram.
As shown in Figure 2 to 4, internal combustion engine 18 obtains power in the following way: crank axle 34 is with the work in cylinder 31
It fills in 32 reciprocating motion and is rotated via crank 33.Also, the crank box of receiving crank 33 and crank axle 34 is provided with storage
Deposit the food tray 35 of working oil (working solution).
The hydraulic device of present embodiment has auxiliary pump 41, clutch 44, hydraulic-driven portion 54 and control unit 55.
Auxiliary pump 41 is driven with the rotation of the crank axle 34 of internal combustion engine 18.Auxiliary pump 41 is the variable of inclined rotor pump etc.
Volumetric pump.As shown in Figure 3 and 4, the crank gear 42 of the crank axle 34 of internal combustion engine 18 is set to the rotation of crank axle 34
Then rotation, thus auxiliary pump 41 come pressure accumulation working oil and improves the hydraulic of working oil using the rotation.
Also, auxiliary pump 41 is provided with more.In the present embodiment, as shown in figure 3, each auxiliary pump 41 relative to song
The transmission gear 43 that handle gear 42 connects connects.
The rotation of crank gear 42 is connected or is cut off relative to each auxiliary pump 41 by clutch 44.That is, each auxiliary pump 41
It is arranged in such a way that the rotation of crank gear 42 is passed via clutch 44 relative to crank gear 42.Such as shown in Fig. 4,
It is connected with transmission gear 43A (43) in crank gear 42, clutch 44 is set to the transmitting connecting with transmission gear 43A (43)
Between gear 43B (43) and auxiliary pump 41, and by connecting or cutting off transmission gear 43B (43) and auxiliary pump 41 for crank tooth
The rotation of wheel 42 is connected or is cut off relative to auxiliary pump 41.Like this, clutch 44 can connect not stopping the rotation of crank axle 34
The rotation of the crank gear 42 relative to each auxiliary pump 41 is connect or cuts off, clutch 44 is configured to switch the operating of each auxiliary pump 41
Or the auxiliary pump switching mechanism stopped.
Also, as shown in Fig. 2, hydraulic device conveys storage by the low-lift pump 52 driven by motor 51 under low pressure
In the working oil of food tray 35, and the working oil is supplied to via adverse current preventing portion 53 suction inlet side of each auxiliary pump 41.Also,
The working oil for becoming high pressure from each 41 pressure accumulation of auxiliary pump is discharged from the outlet of each auxiliary pump 41, and via adverse current preventing portion
53 and be fed into hydraulic-driven portion 54.Here, in internal combustion engine 18 in ship, 34 positive and negative rotation of crank axle, therefore phase therewith
The auxiliary pump 41 of companion also positive reverse action, be consequently inhaled mouth and outlet mutually becomes outlet and suction inlet instead.Adverse current preventing portion
53 are combined by four check-valves 53a and constitute, which acts on as follows: the low pressure that will be conveyed by low-lift pump 52
Working oil be supplied to auxiliary pump 41 suction inlet and by the working oil for the high pressure being discharged from the outlet of auxiliary pump 41 supply
To hydraulic-driven portion 54.
Hydraulic-driven portion 54 is the actuating that the petrolift of fuel or the exhaust valve of driving internal combustion engine 18 are supplied to internal combustion engine 18
The lower part driving valve device of device etc., the hydraulic-driven portion 54 be supplied to and by solenoid valve control in auxiliary pump 41 by pressure accumulation
The working oil of high pressure acts.Although hydraulic-driven portion 54 is represented only as one for convenience in Fig. 2, internal combustion engine 18
For multi cylinder and hydraulic-driven portion 54 is arranged in correspondence with each cylinder.Also, the working oil used in hydraulic-driven portion 54 returns
Return the food tray 35 of internal combustion engine 18.
Control unit 55 is such as central operation device (CPU:Central Processing Unit), mainly controls conduct
The clutch 44 of auxiliary pump switching mechanism.Also, control unit 55 had changed the capacity of auxiliary pump 41 not only to control discharge rate, but also control
The motor 51 of low-lift pump 52, and control the solenoid valve in hydraulic-driven portion 54.Also, control unit 55 passes through internal combustion engine test section
And obtain the load of internal combustion engine 18.For internal combustion engine test section for example comprising rotating speed measuring portion 61, rotating speed measuring portion 61 detects internal combustion engine
The revolving speed of crank axle 34 in 18 based on the revolving speed and is supplied to fuel quantity (the hydraulic drive of internal combustion engine 18 in control unit 55
The aperture of solenoid valve in dynamic portion 54) calculate the load of internal combustion engine 18.Also, control unit 55 is taken by auxiliary pump test section
Obtain the discharge rate of auxiliary pump 41.For auxiliary pump test section for example comprising rotating speed measuring portion 61, rotating speed measuring portion 61 detects internal combustion engine 18
In the revolving speed of crank axle 34 each auxiliary pump 41 is calculated based on the capacity of the revolving speed and auxiliary pump 41 in control unit 55
Discharge rate.Also, control unit 55 obtains total discharge rate of the auxiliary pump 41 operated when calculating.Also, control unit 55 is logical
The gross pressure of excess pressure test section 62 and the working oil after the discharge of whole auxiliary pumps 41 in acquirement operating.Pressure detecting portion 62
It is set to the downstream side of adverse current preventing portion 53, is in particular arranged at the food tray for returning to internal combustion engine 18 in the downstream in hydraulic-driven portion 54
35 part, and detect the pressure for being conveyed through the working oil of the part.
Fig. 5 is the relationship of the engine load (engine loading) and working oil necessary amount that indicate that crank axle often rotates a circle
Curve graph.Fig. 6 is the curve for indicating the relationship of engine load (engine loading) and crankshaft-rotation (engine speed)
Figure.Fig. 7 is the curve graph for indicating the relationship of engine load (engine loading) and working oil necessary amount per unit time.Figure
8 be the curve graph for indicating the relationship of auxiliary pump delivery and the efficiency of pump.Fig. 9 indicates that engine load per unit time (is started
Machine load) curve graph with the relationship of working oil necessary amount and auxiliary pump number of units.
As shown in figure 5, the hydraulic-driven portion 54 in present embodiment has petrolift A, lower part driving valve device B.Petrolift A
More fuel are consumed as engine loading (revolving speed of crank axle 34 and the relationship of fuel quantity) increases, therefore crank axle 34
The working oil necessity quantitative change often to rotate a circle it is more.On the other hand, driving valve device B in lower part is the exhaust valve of driving internal combustion engine 18
Device, therefore the working oil necessary amount of crank axle 34 often to rotate a circle is to be not accompanied by the fixed value of engine loading variation.Cause
This, in the petrolift A and lower part driving valve device B as hydraulic-driven portion 54, the work of crank axle 34 often to rotate a circle
Oily necessary amount becomes more as engine loading increases.That is, the working oil that hydraulic-driven portion 54 is provided by auxiliary pump 41 must
It wants supply amount to become more as engine loading increases, tails off as engine loading reduces.
Also, as shown in fig. 6, the load of internal combustion engine 18 is relative to revolving speed when rotating crank axle 34 in logarithmic increasing
Add.In this way, the load of internal combustion engine 18 per unit time and the relationship of working oil necessary amount become such as figure by Fig. 5 and Fig. 6
Shown in 7.
Here, as shown in figure 8, having when being lower than about 50% with comparable 41 discharge rate of auxiliary pump of working oil necessary amount
The tendency that the efficiency of pump of auxiliary pump 41 reduces.Therefore, in order to improve the efficiency of pump, internal combustion engine per unit time shown in Fig. 7
In 18 load and the relationship of working oil necessary amount, as shown in figure 9, for example using three auxiliary pump 41, inside
The load of combustion engine 18 operates an auxiliary pump 41 and stops two auxiliary pumps 41 when being 40% or less, as a result, internal combustion engine 18
Load it is corresponding with the working oil necessary amount supplied using an auxiliary pump 41 so as to keeping auxiliary pump 41 high in the efficiency of pump
It is operated in region.On the other hand, two auxiliary pumps 41 are operated and make one
Platform auxiliary pump 41 stop, as a result, internal combustion engine 18 load with using two auxiliary pumps 41 supply working oil necessary amount it is corresponding from
And each auxiliary pump 41 can be made to operate in the high range of the efficiency of pump.Consider the efficiency of pump of auxiliary pump 41 and presets auxiliary pump
41 operating number.
In addition, in Fig. 9, although a state in stopping in three auxiliary pumps 41, the auxiliary pump of the stopping
41 as spare the case where other auxiliary pumps 41 break down etc..Also, the number of units of auxiliary pump 41 is not limited in an example
Three.Also, in Fig. 9, change auxiliary pump 41 number of units benchmark " 40% " only an example and be not limited to
This.
Figure 10 is the movement for indicating hydraulic device involved in present embodiment, i.e. the flow chart of the control of control unit.
As shown in Figure 10, control unit 55 obtains the auxiliary pump of load or the load relative to internal combustion engine 18 of internal combustion engine 18
Load condition (step S1) of 41 discharge rate as internal combustion engine 18.Also, it is negative compared to defined in the load of internal combustion engine 18
In the case that load (for example, 40%) reduces (step S2: yes), control unit 55 controls the clutch as auxiliary pump switching mechanism
44, stop defined auxiliary pump 41 to reduce the number of units (step S5) of the auxiliary pump 41 of operating.At this point, carrying out step S5's
Before control, control unit 55 increases the discharge rate (step S3) of the auxiliary pump 41 of operating and reduces the auxiliary pump 41 that will stop
Discharge rate (step S4).On the other hand, when the load of internal combustion engine 18 in step s 2 is compared to defined load (for example, 40%)
In the case where not reducing (step S2: no), if in step s 6, the load of internal combustion engine 18 compared to defined load (for example,
40%) rise (step S6: yes), then control unit 55 controls the clutch 44 as auxiliary pump switching mechanism, makes defined auxiliary
Pump 41 operates to increase the number of units (step S7) of the auxiliary pump 41 of operating.Thereafter, control unit 55 makes the auxiliary pump 41 in operating
The load of discharge rate and internal combustion engine 18 accordingly reduces (step S8) and increases the discharge rate of the auxiliary pump 41 newly operated by (step
Rapid S9).If also, the load of internal combustion engine 18 compared to defined load (for example, 40%) does not rise (step in step s 6
S6: no), then return step S1, control unit 55 obtain the load of internal combustion engine 18 or the load auxiliary pump relative to internal combustion engine 18
Load condition of 41 discharge rate as internal combustion engine 18.In addition, the control periodically or continuously carries out.
Alternatively, it is also possible to being step S6 in step S2 and step S6 preceding.Specifically, it is preferable that from high load to low
In the case that load is mobile in a manner of first carrying out step S2 and reduce the load of internal combustion engine 18 not compared to defined load
Control, first to carry out step S6 and make the load of internal combustion engine 18 compared to regulation in the case where mobile to high load from low-load
The mode that does not rise of load control.
Like this, the hydraulic device of present embodiment has: more auxiliary pumps 41, which passes through internal combustion engine
18 power carries out pressure accumulation movement；Hydraulic-driven portion 54, the hydraulic-driven portion 54 pass through by the hydraulic of each 41 pressure accumulation of auxiliary pump
To drive；And auxiliary pump switching mechanism, the auxiliary pump switching mechanism is according to the load condition of internal combustion engine 18, than defined
Load it is low in the case where reduce the operating number of auxiliary pump 41, and increase auxiliary pump 41 in the case where higher than defined load
The mode of operating number makes auxiliary pump 41 stop or operate.
In addition, auxiliary pump switching mechanism here is the mechanism switched as follows: pair of connection or cutting internal combustion engine 18
The power of auxiliary pump 41 transmits, which includes to be able to carry out switching without stopping the rotation of crank axle 34
Above-mentioned clutch 44, but also including, for example, making nibbling for crank gear 42 and transmission gear 43 in the state of stopping internal combustion engine 18
Close the mechanism being detached from.Also, the load condition of internal combustion engine 18 refers to the load comprising internal combustion engine 18 itself, internal combustion engine 18 is discharged
The discharge rate of the auxiliary pump 41 of work oil mass necessary to load.
It is auxiliary by reducing in the case where the load condition of internal combustion engine 18 is lower than defined load according to the hydraulic device
The operating number of pump 41 is helped, can be operated in each auxiliary pump 41 with the high state of the efficiency of pump.On the other hand, in internal combustion engine 18
Load condition than it is defined load it is high in the case where, by increase auxiliary pump 41 operating number, can be in each auxiliary pump
It is operated in 41 with the high state of the efficiency of pump.The high-efficient of auxiliary pump 41 is used as a result, it is possible to not influenced by engine loading
Region.
Also, in the hydraulic device of present embodiment, auxiliary pump switching mechanism is made of clutch 44, and clutch 44 is set
It is placed between the transfer route that the power of internal combustion engine 18 is transmitted to auxiliary pump 41, and clutch 44 stops internal combustion engine 18
It can connect or cut off the power of the internal combustion engine 18 transmitted to auxiliary pump 41.
According to the hydraulic device, not making internal combustion engine 18 stop to connect or cutting off the internal combustion transmitted to auxiliary pump 41
The power of machine 18, thereby, it is possible to the stopping or operating of auxiliary pump 41 are carried out in the operation of internal combustion engine 18.
Also, has control unit 55 in the hydraulic device of present embodiment, which obtains the negative of internal combustion engine 18
It carries, and controls auxiliary pump switching mechanism in a manner of the operating number to become preset auxiliary pump 41 according to the load.
Alternatively, having control unit 55 in the hydraulic device of present embodiment, which obtains the total of the auxiliary pump 41 in operating
Discharge rate, and control auxiliary pump in a manner of the operating number to become preset auxiliary pump 41 according to total discharge rate and cut
It changes planes structure.
According to the hydraulic device, the operating number of auxiliary pump 41 is automatically controlled by control unit 55, therefore can be shown
Land to obtain not the effect for being influenced and being applicable in the high-efficient region of auxiliary pump 41 by engine loading.
Also, in the hydraulic device of present embodiment, auxiliary pump 41 be the discharge rate of working solution can be made variable can
Varying capacity pump, control unit 55 make the auxiliary pump 41 to be stopped in the case where reducing the operating number of auxiliary pump 41
Discharge rate gradually decreases, and make operating auxiliary pump 41 discharge rate gradually increase after, control auxiliary pump switching mechanism.
The pressure of working oil can be prevented in the case where reducing the operating number of auxiliary pump 41 according to the hydraulic device
Power variation, the torque of auxiliary pump 41 change and carry out the switching of auxiliary pump 41.
Also, in the hydraulic device of present embodiment, auxiliary pump 41 be the discharge rate of working solution can be made variable can
Varying capacity pump, control unit 55 after controlling auxiliary pump switching mechanism, make in the case where making the increased situation of operating number of auxiliary pump 41
The discharge rate of the auxiliary pump 41 newly operated gradually increases, and gradually decreases the discharge rate of the auxiliary pump 41 in operating.
The pressure of working oil can be prevented in the case where making the increased situation of operating number of auxiliary pump 41 according to the hydraulic device
Power variation, the torque of auxiliary pump 41 change and carry out the switching of auxiliary pump 41.
Also, in the hydraulic device of present embodiment, feelings of the control unit 55 in the operating number reduction for making auxiliary pump 41
Under condition, the auxiliary pump 41 different by the auxiliary pump 41 made from upper one time stops controlling auxiliary pump switching mechanism in a manner of stopping.
According to the hydraulic device, the total run time of each auxiliary pump 41 can be made to homogenize and reduce the damage of auxiliary pump 41
Probability.
Also, in the hydraulic device of present embodiment, control unit 55 obtains the working solution after the discharge of each auxiliary pump 41
Gross pressure, and in the case where the preset pressure of the overall pressure ratio is low, in a manner of operating the auxiliary pump 41 stopped
Control auxiliary pump switching mechanism.
Specifically, as described above, indicating that one in three auxiliary pumps 41 is halted state in the flow chart of Figure 11
And as spare situation.That is, control unit 55 is from the working oil after the discharge that pressure detecting portion 62 obtains whole auxiliary pumps 41
Gross pressure (step S21) is lower than the feelings of the pressure of the working oil of the necessary amount that should be obtained as setting value in the gross pressure
Under condition (step S22: yes), the auxiliary pump 41 stopped being made to operate (step S23).If gross pressure is not less than the necessary amount that obtain
Working oil constant pressure (step S22: no), then return step S21 and obtain gross pressure.The control is periodically or continuous
Ground carries out.
It, can be automatically using backup in the case that auxiliary pump 41 in operation breaks down according to the hydraulic device
And obtain the working oil of necessary amount.
Also, in the hydraulic device of present embodiment, control unit 55 makes auxiliary pump using auxiliary pump switching mechanism
In the case that 41 stop or operate, which is maintained into the defined time.
Specifically, control unit 55 have timing unit, made using auxiliary pump switching mechanism auxiliary pump 41 stop or
By timing unit come minute in the case where operating.Also, auxiliary pump switching machine is not controlled until by the stipulated time
Structure.
For example, in navigation in bad weather, when screw rod exposes from the water surface, the load of internal combustion engine 18 or
The discharge rate of the auxiliary pump 41 of work oil mass necessary to the load of internal combustion engine 18 is discharged, i.e. load condition instantaneously changes.Phase
Variation for the load condition of internal combustion engine 18 instantaneous in this way, the operating or stopping for carrying out auxiliary pump 41, which have, dislikes load change
The worry of change.Led to according to the hydraulic device in the case where stopping auxiliary pump 41 by auxiliary pump switching mechanism or operating
It crosses and the state is maintained into the stipulated time, be able to suppress the deterioration of load change.
Also, internal combustion engine 18 of the invention has above-mentioned hydraulic device.
According to the internal combustion engine 18, in hydraulic device, in the load condition of internal combustion engine 18 situation lower than defined load
Under, by reducing the operating number of auxiliary pump 41, can be operated in each auxiliary pump 41 with the high state of the efficiency of pump.Another party
It face, can by increasing the operating number of auxiliary pump 41 in the case where the load condition of internal combustion engine 18 is higher than defined load
It is operated in each auxiliary pump 41 with the high state of the efficiency of pump.Auxiliary is used as a result, it is possible to not influenced by engine loading
The high-efficient region of pump 41, and can be improved the energy efficiency as internal combustion engine 18.
Also, the ship of present embodiment has above-mentioned internal combustion engine 18.
According to the ship, in hydraulic device, in the case where the load condition of internal combustion engine 18 is lower than defined load, lead to
The operating number for reducing auxiliary pump 41 is crossed, can be operated in each auxiliary pump 41 with the high state of the efficiency of pump.On the other hand, exist
It, can be each by increasing the operating number of auxiliary pump 41 in the case that the load condition of internal combustion engine 18 is higher than defined load
It is operated in a auxiliary pump 41 with the high state of the efficiency of pump.Auxiliary pump 41 is used as a result, it is possible to not influenced by engine loading
High-efficient region, and can be improved the energy efficiency as internal combustion engine 18 and ship entirety.
Symbol description
10 hulls
18 internal combustion engines
41 auxiliary pumps
44 clutches
54 hydraulic-driven portions
55 control units
61 rotating speed measuring portions
62 pressure detecting portions
Claims (11)
1. a kind of hydraulic device, which is characterized in that have:
More auxiliary pumps, the more auxiliary pumps carry out pressure accumulation movement by the power of internal combustion engine；
Hydraulic-driven portion, the hydraulic-driven portion by the hydraulic of each auxiliary pump pressure accumulation by being driven；And
Auxiliary pump switching mechanism, the auxiliary pump switching mechanism is according to the load condition of the internal combustion engine, than defined load
The operating number of the auxiliary pump is reduced in the case where low, and increases the auxiliary pump in the case where higher than defined load
The mode of operating number makes the auxiliary pump stop or operate.
2. hydraulic device according to claim 1, which is characterized in that
The auxiliary pump switching mechanism is made of clutch, and the clutch, which is set to, is transmitted to institute for the power of the internal combustion engine
It states between the transfer route of auxiliary pump, and the clutch is not making the internal combustion engine stopping that capable of connecting or cut off to institute
State the power of the internal combustion engine of auxiliary pump transmitting.
3. hydraulic device according to claim 1, which is characterized in that
It is also equipped with control unit, which obtains the load of the internal combustion engine, and to become preset according to the load
The mode of the operating number of the auxiliary pump controls the auxiliary pump switching mechanism.
4. hydraulic device according to claim 1, which is characterized in that
It is also equipped with control unit, which obtains total discharge rate of the auxiliary pump in operating, and according to total discharge rate
And the mode for becoming the operating number of the preset auxiliary pump controls the auxiliary pump switching mechanism.
5. hydraulic device according to claim 3 or 4, which is characterized in that
The auxiliary pump is the variable displacement pump that the discharge rate of working solution can be made variable,
The control unit makes the auxiliary pump to be stopped in the case where reducing the operating number of the auxiliary pump
Discharge rate gradually decreases, and make operating the auxiliary pump discharge rate gradually increase after, control the auxiliary pump switching machine
Structure.
6. hydraulic device according to claim 3 or 4, which is characterized in that
The auxiliary pump is the variable displacement pump that the discharge rate of working solution can be made variable,
The control unit after controlling auxiliary pump switching mechanism, makes in the case where making the increased situation of operating number of the auxiliary pump
The discharge rate of the auxiliary pump newly operated gradually increases, and gradually decreases the discharge rate of the auxiliary pump in operating.
7. hydraulic device according to claim 3 or 4, which is characterized in that
The control unit is in the case where reducing the operating number of the auxiliary pump, so that the auxiliary stopped with upper one time
It pumps the mode that the different auxiliary pumps stops and controls the auxiliary pump switching mechanism.
8. hydraulic device according to claim 3 or 4, which is characterized in that
The control unit obtains the gross pressure of the working solution after the discharge of each auxiliary pump, and presets in the overall pressure ratio
Pressure it is low in the case where, by make stop the auxiliary pump operating in a manner of control the auxiliary pump switching mechanism.
9. hydraulic device according to claim 3 or 4, which is characterized in that
The control unit using the auxiliary pump switching mechanism in the case where making the auxiliary pump stop or operate by the shape
State maintains the defined time.
10. a kind of internal combustion engine, which is characterized in that
Has hydraulic device according to any one of claims 1 to 9.
11. a kind of ship, which is characterized in that
Has internal combustion engine described in any one of claim 10.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015009749A JP6452466B2 (en) | 2015-01-21 | 2015-01-21 | Hydraulic device, internal combustion engine and ship |
| JP2015-009749 | 2015-01-21 | ||
| PCT/JP2015/073895 WO2016117156A1 (en) | 2015-01-21 | 2015-08-25 | Hydraulic device, internal combustion engine, and ship |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107208624A CN107208624A (en) | 2017-09-26 |
| CN107208624B true CN107208624B (en) | 2019-01-08 |
Family
ID=56416719
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580073785.8A Expired - Fee Related CN107208624B (en) | 2015-01-21 | 2015-08-25 | hydraulic device, internal combustion engine and ship |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6452466B2 (en) |
| KR (1) | KR101927649B1 (en) |
| CN (1) | CN107208624B (en) |
| WO (1) | WO2016117156A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7344019B2 (en) * | 2019-06-24 | 2023-09-13 | 株式会社ジャパンエンジンコーポレーション | Marine internal combustion engine |
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| US4763473A (en) * | 1986-04-07 | 1988-08-16 | O&K Orenstein & Koppel Aktiengesellschaft | Arrangement for operating a diesel hydraulic drive |
| JP2000291563A (en) * | 1999-04-06 | 2000-10-17 | Kobelco Contstruction Machinery Ltd | Pump control device for work machine |
| JP2005282577A (en) * | 1997-05-21 | 2005-10-13 | Man B & W Diesel As | Hydraulic device |
| CN101313155A (en) * | 2005-11-25 | 2008-11-26 | 日立建机株式会社 | Pump torque controller of hydraulic working machine |
| CN100520022C (en) * | 2002-12-11 | 2009-07-29 | 日立建机株式会社 | Method and device for controlling pump torque for hydraulic construction machine |
| JP4975986B2 (en) * | 2005-07-29 | 2012-07-11 | スズキ株式会社 | Failure diagnosis device for downstream exhaust gas sensor |
| CN102734447A (en) * | 2011-03-30 | 2012-10-17 | 日立汽车系统株式会社 | Electric oil pump |
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| JPS4975986A (en) * | 1972-11-27 | 1974-07-22 | ||
| JP3074285B2 (en) * | 1990-06-21 | 2000-08-07 | セイコー精機株式会社 | Cogeneration equipment |
| JPH07119624A (en) * | 1993-10-18 | 1995-05-09 | Mazda Motor Corp | Oil pump device for engine |
| JP4010428B2 (en) * | 1998-07-13 | 2007-11-21 | 株式会社小松製作所 | Capacity control device for work vehicle pump |
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2015
- 2015-01-21 JP JP2015009749A patent/JP6452466B2/en not_active Expired - Fee Related
- 2015-08-25 CN CN201580073785.8A patent/CN107208624B/en not_active Expired - Fee Related
- 2015-08-25 WO PCT/JP2015/073895 patent/WO2016117156A1/en active Application Filing
- 2015-08-25 KR KR1020177020202A patent/KR101927649B1/en active IP Right Grant
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4763473A (en) * | 1986-04-07 | 1988-08-16 | O&K Orenstein & Koppel Aktiengesellschaft | Arrangement for operating a diesel hydraulic drive |
| JP2005282577A (en) * | 1997-05-21 | 2005-10-13 | Man B & W Diesel As | Hydraulic device |
| JP2000291563A (en) * | 1999-04-06 | 2000-10-17 | Kobelco Contstruction Machinery Ltd | Pump control device for work machine |
| CN100520022C (en) * | 2002-12-11 | 2009-07-29 | 日立建机株式会社 | Method and device for controlling pump torque for hydraulic construction machine |
| JP4975986B2 (en) * | 2005-07-29 | 2012-07-11 | スズキ株式会社 | Failure diagnosis device for downstream exhaust gas sensor |
| CN101313155A (en) * | 2005-11-25 | 2008-11-26 | 日立建机株式会社 | Pump torque controller of hydraulic working machine |
| CN102734447A (en) * | 2011-03-30 | 2012-10-17 | 日立汽车系统株式会社 | Electric oil pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6452466B2 (en) | 2019-01-16 |
| JP2016133093A (en) | 2016-07-25 |
| WO2016117156A1 (en) | 2016-07-28 |
| CN107208624A (en) | 2017-09-26 |
| KR101927649B1 (en) | 2018-12-10 |
| KR20170096041A (en) | 2017-08-23 |
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Granted publication date: 20190108 |