JP3806398B2 - Cylinder lubrication device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a cylinder lubrication device that performs forced lubrication on a cylinder of an internal combustion engine, particularly a large diesel engine, preferably a marine diesel engine.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, there has been known a mechanical cylinder lubricator that interlocks a plunger pump with an engine crankshaft and lubricates the lubricating oil pumped from the pump into an engine cylinder through an injector with a check valve ( For example, see Patent Document 1.)
[0003]
In this cylinder lubricator, the cam of the camshaft that is rotated using the power of the engine is used to swing the rocker arm, and the plunger pump plunger is supported at one end of this arm, and the plunger is attached in the return direction by a spring. It is fast. One or more injectors communicate with the oil outlet of the plunger pump, and these injectors are attached to the cylinder of the engine. Thus, when the plunger is reciprocated in the axial direction along with the rotation of the cam and the pump operation is performed, lubricating oil is injected into the cylinder through each injector and injected.
[0004]
Adjustment of oiling in a conventional cylinder oiling machine is performed by changing the effective stroke of the plunger by moving the oil amount adjusting screw abutted against the other end of the rocker arm forward and backward.
[0005]
[Patent Document 1]
Microfilm (No. 1 to No. 3, Fig. 1 and Fig. 2) of No. 56-71004 (No. 59-175619)
[0006]
[Problems to be solved by the invention]
Since one mechanical cylinder lubricator of Patent Document 1 is usually required for one cylinder of an engine, a number of cylinder lubricators corresponding to the number of cylinders should be installed side by side so that they can be used synchronously. Thus, a cylinder oiling device is configured. An installation example of a plurality of cylinder lubricators is shown in FIG. In FIG. 11, reference numeral 1 is an engine having a plurality of cylinders 2, reference numeral 3 is a cylinder lubricator having the above-described configuration, reference numeral 4 is a camshaft, reference numeral 5 is a cam, reference numeral 6 is a shaft coupling, reference numeral 7 is a chain or gear transmission. Each mechanism is shown. The camshaft 4 penetrates the box-shaped lubricator main body 3 a in which the lubricating oil of the cylinder lubrication device 3 is stored in the horizontal direction, and the camshafts 4 adjacent to each other in the axial direction are connected by a shaft coupling 6. One end of the camshaft group connected by this connection and the camshaft of an exhaust valve (not shown) of the engine 1 are connected by a chain or a gear transmission mechanism 7.
[0007]
By the way, for example, some marine engines have a length of more than a dozen meters, so that the length of the camshaft group becomes long according to the length of the engine. In this case, if the axes of the cam shafts 4 are not aligned, torque imbalance occurs and the timing of lubrication is adversely affected. Therefore, when installing each cylinder lubricator 3 to prevent this from happening, it is necessary to perform a large number of connecting operations using the shaft coupling 6, and the cam shafts 4 must be aligned. However, these operations are time consuming.
[0008]
Further, after the plurality of cylinder lubricators 3 are installed so as to be interlocked with each other, it is necessary to match the amount of lubrication of each injector. Since this adjustment is executed by moving the oil amount adjusting screw forward and backward for each cylinder lubricator 3 and changing the effective stroke of the plunger, it takes time and effort.
[0009]
In addition, it is difficult to change the amount of oil injected into the injector during engine operation, and the fixed amount of oil determined by the plunger stroke is made regardless of the engine load. It is also difficult to do. For this reason, when the load of the engine is low, for example, there is a tendency that more oil than necessary is wasted.
[0010]
The problem to be solved by the present invention is to obtain a cylinder oiling device that is easy to install in an engine and has excellent oiling controllability.
[0011]
[Means for Solving the Problems]
  In order to solve the above-mentioned problems, the present invention provides an injector that is attached to a plurality of cylinders of an engine and injects and supplies lubricating oil into the cylinder, a lubricating oil pump that pumps lubricating oil, and a discharge of the pump. A common oil feeding section provided in communication with the opening and storing the lubricating oil in a pressurized state; a plurality of branch oil feeding pipes branched from the common oil feeding section and connected to the injectors; A normally-closed electromagnetic on-off valve provided in each oil pipe, and an electronic control device for remotely controlling the opening timing and the open-maintenance time of these electromagnetic on-off valves individually.Equipped,
  An oil amount limiter is provided in each of the branch oil supply pipes, and the oil amount limiter communicates the oil inlet and the oil outlet with a housing having an oil chamber and an oil inlet and an oil outlet communicating with the oil chamber. A shuttle having a throttle passage and reciprocally moved between a first position away from the oil inlet and a second position seated on the oil inlet, and the shuttle directed to the first position And a biasing body that biasesIt is characterized by that.
  In a preferred embodiment of the present invention, the oil amount limiter includes a lift sensor that detects movement of the shuttle..
  Similarly, in the preferable form of this invention, the said housing is provided with the transparent window which makes the said oil chamber visible.
  Similarly, in a preferred embodiment of the present invention, the control device includes a shuttle determination unit that determines whether or not the shuttle is operating properly based on a detection signal output from the lift sensor..
  Similarly, in a preferred embodiment of the present invention, the control device includes a shuttle movement amount calculation unit that calculates a movement amount of the shuttle based on a detection signal output from the lift sensor..
[0012]
In a preferred embodiment of the present invention, a plurality of the electromagnetic on-off valves can be provided in parallel to the branch oil supply pipe.
[0013]
Similarly, in the preferable form of this invention, the said electromagnetic on-off valve can be integrated in the said injector.
[0014]
Similarly, in a preferred embodiment of the present invention, the branch oil feeding pipe has one upstream piping section with the electromagnetic on-off valve as a boundary and is connected to the common oil feeding section, and downstream with the electromagnetic on-off valve as a boundary. The side branch oil supply pipe part is branched into a plurality of parts, and the injectors can be individually connected to each of the downstream side branch oil supply pipe parts.
[0015]
Similarly, in a preferred mode of the present invention, the downstream branch oil feed pipe portion other than the downstream branch oil feed pipe portion having the longest pipe length in the downstream branch oil feed pipe portion is in accordance with the pipe length. A diaphragm can be provided.
[0018]
Similarly, in a preferred embodiment of the present invention, the electronic control device can control the valve opening timing and the valve opening maintaining time based on the crank angle detection signal of the engine input thereto.
[0019]
Similarly, in a preferred embodiment of the present invention, the electronic control device can control the valve opening maintaining time based on an engine load signal input thereto.
[0020]
Similarly, in a preferred embodiment of the present invention, the electronic control unit sets the valve opening maintenance time based on cylinder temperatures detected by a plurality of temperature sensors attached to the cylinder at intervals along the circumferential direction. Can be controlled.
[0021]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.
[0022]
Reference numerals 11a to 11n in FIG. 1 (in FIG. 1, only 11a and 11n positioned on the end side in the arrangement direction are illustrated, and the others are not illustrated), and a plurality of large diesel engines for ships are provided. The cylinder is shown. Each of the cylinders 11a to 11n has a plurality of, for example, six injectors 12a to 12f (for example, six injectors 12a to 12f (e.g., equally arranged in the circumferential direction) at a predetermined lubrication point (for example, a height position of 1/3 or more of the cylinder liner height) In FIG. 1, only three injectors 12a to 12c are shown, and the others are not shown. Each of the injectors 12a to 12n may be a check valve type, an inner opening valve type capable of high-speed injection than the check valve type, or a mixture thereof. .
[0023]
The check valve type injector is provided with an oil chamber, an injection hole communicating with the oil chamber, and a tapered valve seat forming a part of the inner surface of the oil chamber at the tip of the nozzle body. An oil introduction passage that opens in the center of the nozzle body is provided so as to extend in the axial direction in the center of the nozzle body, and a check valve such as a steel ball that contacts and separates from the valve seat in the oil chamber, A coil spring that is pressed toward the housing is housed. In this injector, when the pressure of the lubricating oil introduced into the oil introduction passage becomes larger than the biasing force of the coil spring, the check valve is separated from the valve seat, and the lubricating oil flowing into the oil chamber is Lubricate by being injected into. This lubrication is stopped when the pressure of the lubricating oil introduced into the oil introduction passage is reduced.
[0024]
The inner opening valve type injector has an oil chamber at the tip of the nozzle body, an injection hole communicating with the oil chamber, and a valve seat between them, and has a seat surface that contacts and separates from the valve seat. The needle is accommodated in the nozzle body so as to be movable in the axial direction, the needle is pressed against the valve seat by a coil spring, and an oil introduction passage is provided in the nozzle body so as to avoid the needle and communicate with the oil chamber. . This injector is guided to the oil introduction passage, and when the pressure of the lubricating oil applied to the seat surface becomes larger than the urging force of the coil spring, the needle is separated from the valve seat and the lubricating oil flowing into the oil chamber is injected into the injection hole. Lubricate by being injected from the outside. This lubrication is stopped when the pressure of the lubricating oil introduced into the oil introduction passage is reduced.
[0025]
The injection holes of the injectors 12a to 12n facing the inside of any of the cylinders 11a to 11n may be single holes suitable for injecting lubricating oil in the radial direction of the cylinders 11a to 11n, but may be formed on the inner peripheral surfaces of the cylinders 11a to 11n. It may be a double hole suitable for injecting lubricating oil along.
[0026]
In each of the cylinders 11a to 11n, a plurality of preferably the same number of temperature sensors (hereinafter abbreviated as sensors) 13a to 13n as the injectors 12a to 12n (only 13a to 13c are shown in FIG. 1, and the others are not shown). Is installed). The sensors 13a to 13n are arranged close to the injectors 12a to 12n so as to individually correspond to the injectors 12a to 12n. These sensors 13a-13n detect the temperature of each measurement position in the circumferential direction of each cylinder 11a-11n in which a piston (not shown) reciprocates, and output it as an electrical signal.
[0027]
The injectors 12a to 12n and the sensors 13a to 13n, the lubricating oil pump (hereinafter abbreviated as a pump) 14 shown in FIG. 1, a common oil feeding pipe 15 as a common oil feeding part, and a plurality of branch oil feeding pipes 16a. To 16n, a plurality of electromagnetic on-off valves (hereinafter abbreviated as electromagnetic valves) 17a to 17n, a plurality of oil amount limiters 18a to 18n, and a piezo-electric control device 19, and the electronic control of the present invention. A cylinder lubrication device 20 of the type is formed.
[0028]
For example, a constant displacement hydraulic pump having a one-way flow can be suitably used as the pump 14 that is driven by transmission of electric or rotation of a rotating part of the engine. A common oil feed pipe 15 communicates with a discharge port of a pump 14 from which lubricating oil (also referred to as cylinder oil) is discharged. The common oil supply pipe 15 is routed along the arrangement of the cylinders 11a to 11n of the engine. The common oil feeding pipe 15 has a predetermined internal volume so as to function as a common rail, and the lubricating oil pumped from the pump 14 can be maintained and stored in a pressurized state in which a predetermined pressure is maintained. . The common oil feeding pipe 15 is arranged so as to cover all the cylinders 11a to 11n. Alternatively, the common oil feeding pipe 15 may be provided for each of the cylinders 11a to 11n, or may be arranged for each of a plurality of adjacent cylinders. It is.
[0029]
The branch oil supply pipes 16a to 16n are provided in the same number as the injectors 12a to 12n provided for each cylinder 11a to 11n. One end of each of the branch oil supply pipes 16a to 16n is connected to the common oil supply pipe 15, and the other end is individually connected to the injectors 12a to 12n so as to guide the lubricating oil to the oil introduction passage.
[0030]
The electromagnetic valves 17a to 17n are individually attached in the middle of the branch oil supply pipes 16a to 16n. These electromagnetic valves 17a to 17n are general-purpose valves that are normally closed, and a 2-port 2-position switching valve illustrated in FIG. 2 can be preferably used. By opening these solenoid valves 17a to 17n by remote control, the pressure oil in the common oil feed pipe 15 is guided to the injectors 12a to 12n through the branch oil feed pipes 17a to 17n, and can be lubricated. It is possible to stop the lubrication by setting the state.
[0031]
The oil amount limiters 18a to 18n are individually attached in the middle of the branch oil supply pipes 16a to 16n. Each of the oil amount limiters 18a to 18n limits the amount of lubricating oil supplied to the injectors 12a to 12n, and is configured as illustrated in FIG.
[0032]
Specifically, each of the oil amount limiters 18a to 18n includes a housing 31, a shuttle 32, and a coil spring 33 as an urging member.
[0033]
The cylindrical housing 31 is formed by providing a ring-shaped transparent window 31c between the first and second housing elements 31a and 31b, and has an oil chamber 34 that is visible through the transparent window 31c. Since the shuttle 32 in the housing 31 can be visually recognized by the transparent window 31c, it is suitable when the operation of the shuttle 32 is visually monitored as necessary.
[0034]
The first housing element 31 a communicates with the oil chamber 34 and has an oil inlet 35 that is considerably smaller in diameter than the oil chamber 34. The oil inlet 35 communicates with the common oil feed pipe 15. The second housing element 31 b communicates with the oil chamber 34 and has an oil outlet 36 that is considerably smaller in diameter than the oil chamber 34. The oil outlet 36 is communicated with one of electromagnetic valves 17a to 17n corresponding to one of the injectors 12a to 12n. A portion of the oil outlet 36 facing the oil chamber 34 forms a tapered valve seat 36a.
[0035]
The shuttle 32 is slidably accommodated in the axial direction of the housing 31 along the inner peripheral surface of the oil chamber 34. The shuttle 32 is made of a steel material in a stepped cylindrical shape, and has a throttle passage 37 penetrating in the axial direction. The throttle passage 37 is formed by a first hole portion 37a having the same diameter as the oil inlet 35 and the oil outlet 36, and a second hole portion 37b having a smaller diameter. A small-diameter side end portion 32a of the shuttle 32 approaching the oil outlet 36 is tapered and is brought into contact with and separated from the valve seat 36a.
[0036]
The coil spring 33 is housed in the oil chamber 34 while being compressed between the step 32b of the shuttle 32 and the second housing element 31b. Due to the force of the spring 33, the shuttle 32 is urged in a direction in which the small-diameter-side tip portion 32a is separated from the valve seat 36a.
[0037]
Furthermore, as a preferred example, a lift sensor 38 for detecting the movement of the shuttle 32 is attached to each of the oil amount limiters 18a to 18n. As the sensor 38, a proximity type magnetic sensor or the like can be suitably used. The lift sensor 38 detects a shoulder 32c of the shuttle 32, for example. The shoulder portion 32c is configured such that the small-diameter side distal end portion 32a of the shuttle 32 is connected to the valve seat 36a from the first position (see the state of FIG. 4) where the shuttle 32 is pressed and held on the oil inlet 35 side by the force of the coil spring 33. It is detected by the lift sensor 38 when it is hydraulically moved to the seated second position. Detection signals from the lift sensors 38 are input to the control device 19.
[0038]
The control device 19 is made of a microcomputer or the like, and the operation of the pump 14 and the valve opening timing and the valve opening maintaining time of each electromagnetic valve 17a to 17n are individually synchronized or asynchronously based on various inputs. It is something to control. In addition to the detection signals of the lift sensors 38, the input to the control device 19 includes the detection temperatures (cylinder temperature signals) of the sensors 13a to 13n, the engine crank angle signal, the engine load signal, etc. as shown in FIG. Can be mentioned.
[0039]
The crank angle signal is detected by crank angle detection means 39. This detection means 39 is made up of a detected part such as a projection or a magnet provided on the crankshaft of the engine and a proximity switch for detecting this, for example, one or a plurality of detection pulses (one or more times per one rotation of the crankshaft 3) and is supplied to the control device 19. The engine load signal is generated using an engine load calculation unit 40 that obtains the crank rotation speed from the crank angle signal and calculates whether the engine load is high or low from this rotation speed. The output (engine load signal) of the calculation unit 40 is supplied to the control device 19.
[0040]
Next, the lubrication operation for the cylinders 11a to 11n will be described. When the engine is driven, a crank angle signal detected by the crank angle detecting means 39 is given to the control device 19. Accordingly, the control device 19 excites the electromagnetic valves 17a to 17n at an appropriate time t1 (see FIG. 3) from the rise of the crank angle signal, and opens the electromagnetic valves 17a to 17n. After maintaining the valve open state for an appropriate time from this point, the solenoid valves 17a to 17n are de-energized to be closed.
[0041]
When the electromagnetic valves 17a to 17n are opened by such remote control, the lubricating oil already stored in the predetermined pressure state in the common oil supply pipe 15 passes through the branch oil supply pipes 16a to 16n. The fuel is led to injectors 12a to 12n individually connected to the oil supply pipes 16a to 16n. Thereby, lubricating oil is injected into cylinder 11a-11n from the front-end | tip of each injector 12a-12n, and lubrication is performed. This lubrication is stopped when the solenoid valves 17a to 17n are closed. And in the control apparatus 19, the amount of lubrication can be adjusted by changing the time from the valve opening start of the solenoid valves 17a-17n to the valve closing end, ie, valve opening maintenance time t2 (refer FIG. 3).
[0042]
As described above, the electronic control device 19 remotely controls the valve opening timing and the valve opening maintaining time of the electromagnetic valves 17a to 17n on the basis of the crank angle detection signal input thereto, so that it operates with the engine crank. The electromagnetic valves 17a to 17n can be opened and closed in synchronization with the movement of the piston, and an appropriate amount of lubricating oil can be injected into the cylinders 11a to 11n at an appropriate time.
[0043]
In this case, oil quantity limiters 18a to 18n are interposed in the branch oil supply pipes 16a to 16n, respectively. As a result, the shuttle 32 moves in the direction of the oil outlet 36 due to the oil pressure that has spread to the throttle passage 37 of the shuttle 32 via the oil inlets 35 of the oil amount limiters 18a to 18n, and the small-diameter side end portion 32a of the shuttle 32 eventually becomes oil. Sitting on the valve seat 36a of the outlet 36, the amount of oil is limited from this point.
[0044]
However, the lubricating oil to be injected into the cylinders 11a to 11n is the lubricating oil already filled in the oil chamber 34 compressed by the shuttle 32 as the shuttle 32 moves as described above, and the oil amount is limited. The control device 19 controls the times t1 and t2 so that the lubrication is completed before the operation starts. For this reason, the oil amount limiters 18a to 18n do not hinder the lubrication. When the solenoid valves 17a to 17n are closed and the lubricating oil does not flow, the shuttle 32 is pushed back by the coil spring 33. In this case, the amount of lubricating oil passing through the oil chamber 34 is small with respect to the throttle passage 37. The shuttle 32 is pushed back slowly.
[0045]
Further, since the engine load signal generated from the crank angle signal through the engine load calculation unit 40 is input to the control device 19, the control device 19 opens the electromagnetic valves 17a to 17n based on the engine load signal. The valve maintenance time t2 can be remotely controlled to change the amount of oil injected from each of the injectors 12a to 12n. In other words, since the engine load signal indicates the state of the engine load, for example, when the crankshaft increases and the engine load increases, the engine load signal, which is the calculation result corresponding thereto, is output to the control device 19. Is input.
[0046]
For this reason, the optimum value of the lubrication amount is read from the load table that defines the relationship between the engine load and the lubrication amount set in advance in the storage unit of the control device 19 in accordance with the signal level of the input engine load signal. The valve opening maintaining time t2 can be changed so that the amount of lubrication is obtained. As a result, as the engine load increases, the amount of oil supplied to the cylinders 11a to 11n can be increased, and appropriate oiling according to the engine load is possible.
[0047]
In addition, since the cylinder temperature signals detected by the temperature sensors 13a to 13n attached to the cylinders 11a to 11n are input to the control device 19, the control device 19 uses the temperature signals to control the solenoid valves 17a to 17n. The valve opening maintenance time t2 for each 17n can be remotely controlled individually, and the amount of oil injected from each of the injectors 12a to 12n can be individually changed.
[0048]
In other words, the cylinder temperature signal indicates how the temperature of each part of the cylinder is, so that the part of the cylinder temperature signal input to the controller 19 is detected in a part where a temperature higher than the other part is detected. In accordance with the signal level, the optimum lubrication amount value is read out from the temperature table that defines the relationship between the cylinder temperature and the lubrication amount preset in the storage unit of the control device 19 so that this lubrication amount is obtained. It is possible to change the valve opening maintaining time t2.
[0049]
As a result, a larger amount of lubricating oil can be supplied to the injector located in the portion where the cylinder temperature is higher than the other injectors, and the cylinder can be lubricated. In general, it is conceivable that the portion that is insufficiently lubricated generates frictional heat and the temperature rises too much, causing seizure. On the other hand, as described above, the valve opening maintaining time t2 for the corresponding electromagnetic valve is remotely controlled by the control device 19 based on the temperature of each part of the cylinder, so that it is positioned corresponding to the high temperature portion of the cylinder. As the injector increases the amount of lubrication, it is possible to lubricate appropriately according to the temperature of each part of the cylinder.
[0050]
  Further, as described above, since the oil amount limiters 18a to 18n are individually provided in the respective branch oil supply pipes 16a to 16n, any one of the electromagnetic valves 17a to 17n has failed and stopped in the open state. In this case, for the oil amount limiter provided in series with the solenoid valve, the shuttle 32 moves to close the second position, that is, the oil outlet 36 of the housing 31 by the oil pressure exerted from the common oil feeder 5. Is done. Thereby, it is suppressed that the high-pressure lubricating oil stored in the common oil feeding pipe 15 is lubricated without passing through the failed solenoid valve, and the reliability of the lubrication operation is excellent. When the shuttle 32 is arranged at the second position,Lubricating oil passes through the throttle passage 37.Although it passes, this spillage is small so it is not a problem.
[0051]
  In addition, each of the oil amount limiters 18 a to 18 n includes a lift sensor 38 that detects the movement of the shuttle 32, and a detection signal output from the lift sensor 38 is input to the control device 19. For this reason, in the control device 19, it is possible to determine, for example, whether the shuttle 32 is operating properly by the shuttle determination unit, thereby automatically determining whether the solenoid valves 17a to 17n are functioning normally. Can be monitored automatically. In addition, the control device 19 can calculate the movement amount of the shuttle 32 by the shuttle movement amount calculation unit. Thereby, it is also possible to use this calculation result as a feedback signal for the lubrication amount control for obtaining the timing for closing the solenoid valves 17a to 17n. As described above, the control device 19 includes various processing units such as a shuttle determination unit and a shuttle movement amount calculation unit to obtain a signal useful for monitoring the lubrication status and controlling lubrication.variousThe signal of the lift sensor 38 can be used for the purpose.
[0052]
As described above, the cylinder lubrication device 20 can lubricate the cylinders 11a to 11n at an appropriate timing by changing the valve opening timing of the solenoid valves 17a to 17n by remote control even during operation of the engine. Further, by changing the valve opening maintenance time t2 of the electromagnetic valves 17a to 17n by remote control, the amount of lubrication from the injectors 12a to 12n to the cylinders 11a to 11n can be adjusted, and the lubrication controllability is excellent.
[0053]
Moreover, the cylinder lubrication device 20 having the above-described configuration extends the oil feeding system including the common oil feeding pipe 15 and the branched oil feeding pipes 16a to 16n to the pump 14 and the injectors 12a to 12n attached to the cylinders 11a to 11n of the engine. They are routed around. Therefore, as in the case of using a conventional mechanical cylinder oiling machine, the cylinder oiling device 20 can be provided by routing the piping system without requiring troublesome connection using the shaft coupling and the trouble of aligning the shaft center. Can be installed in the engine easily and at low cost.
[0054]
Next, second to fourth embodiments of the present invention will be described. Since these embodiments basically have the same configuration as that of the first embodiment, the same components are denoted by the same reference numerals as those of the first embodiment, description of the configuration and operation thereof will be omitted, and different portions will be described below. Will be described.
[0055]
In the second embodiment of the present invention shown in FIGS. 5 and 6, a plurality of, for example, two electromagnetic valves 17 a to 17 n that are individually attached to the branch oil supply pipes 16 a to 16 n are provided in parallel instead of one. Yes.
[0056]
Except for this point, the configuration is the same as that of the first embodiment including portions not shown in FIGS. 5 and 6. Therefore, the same effect as the first embodiment can be obtained in the second embodiment. In addition, as described above, two solenoid valves 17 (representative numbers of the solenoid valves 17a to 17n) are provided in parallel for each system of the branch oil supply pipes 16a to 16n. Even if the valve 17 breaks down, lubrication can be secured through the other normal electromagnetic valve 17. Thereby, the reliability of the oiling operation can be ensured.
[0057]
In the third embodiment of the present invention shown in FIGS. 7 and 8, the electromagnetic valves 17a to 17n are individually incorporated in the corresponding injectors 12a to 12n, and the electromagnetic valves 17a to 17n are connected to the branch oil supply pipes 16a to 16n. It is provided at the end. 8A and 8B show the configuration of the injector 12 (representative number of the injectors 12a to 12n) in which the electromagnetic valve is built.
[0058]
In the pilot-type injector 12 shown in FIG. 8A, an oil chamber 42, an injection hole 43 communicating with the oil chamber 42, and a valve seat 44 are provided at the tip of the nozzle body 41, A needle 45 having a conical seat surface 45a contacting and separating from the valve seat 44 is accommodated in a guide hole 41a of the nozzle body 41 so as to be movable in the axial direction. An inlet side of a pilot passage 46 provided in the nozzle body 41 so as to communicate with the oil chamber 42 is provided so as to communicate with the guide hole 41a via the throttle 46a so as to apply a back pressure to the needle 45. In the nozzle body 41, an electromagnetic valve 17 (representative number of the electromagnetic valves 17 a to 17 n) having an exciting coil 47 and an armature 48 is built in series on the axial extension of the needle 45. The armature 48 is urged toward the needle 45 by a coil spring 50 built in the oil introduction passage 49 of the nozzle body 41. The armature 48 can move against the coil spring 50 within the gap G as the exciting coil 47 is excited. The oil chamber 52 in which the needle-side tip of the armature 48 is inserted is communicated with the guide hole 41 a through the small hole 51. The armature 48 has a communication hole 48 a that allows the oil introduction passage 47 and the oil chamber 50 to communicate with each other, and the tip of the armature 48 closes the small hole 51 when the solenoid valve 17 is not excited.
[0059]
The pilot injector 12 in which such an electromagnetic valve 17 is incorporated excites the electromagnetic valve 17 and moves the armature 48 by the gap G, thereby lifting the needle 45 and causing the cylinders 11a to 11a by injection from the injection hole 43. In addition to being able to lubricate into 11n, it is possible to stop the injection by stopping the injection from the injection hole 43 by stopping the excitation. Since this injector 12 can apply a pilot pressure from the pilot passage 46 to the oil chamber 42, a high-speed response is possible. For this reason, it is suitable for lubrication when a short lubrication period is required.
[0060]
Further, in the direct acting injector 12 shown in FIG. 8B, an oil chamber 42, an injection hole 43 communicating with the oil chamber 42, and a valve seat 44 between them are formed at the tip of the nozzle body 41. The needle-shaped armature 55 having a conical seat surface that contacts and separates from the valve seat 44 is accommodated in the guide hole 41a of the nozzle body 41 so as to be movable in the axial direction. The nozzle body 41 incorporates an excitation coil 47 that constitutes the solenoid valve 17 (representative number of the solenoid valves 17a to 17n) together with the armature 55. The armature 55 is urged so as to be pressed against the valve seat 44 by a coil spring 50 built in the oil introduction passage 49 of the nozzle body 41. The armature 55 has a communication hole 55 a that allows the oil introduction passage 49 and the oil chamber 42 to communicate with each other, and the armature 55 moves against the coil spring 49 in the range of the gap G as the excitation coil 47 is excited. Is possible.
[0061]
The direct acting injector 12 in which the electromagnetic valve 17 is incorporated excites the electromagnetic valve 17 to lift the armature 55 by the gap G so as to be able to lubricate by injection from the injection hole 43, and to inject by stopping the excitation. Lubrication can be stopped by stopping injection from the holes 43. This injector 12 is preferable in that the structure is simpler and the cost is lower than that of the pilot injector 12 shown in FIG.
[0062]
The configuration other than the points described above is the same as that of the first embodiment including the portions not shown in FIGS. 7 and 8. Therefore, the third embodiment can obtain the same effects as the first embodiment. In addition, since the electromagnetic valves 17a to 17n are incorporated in the injectors 12a to 12n, the electromagnetic valve 17 and the injector 12 approach each other, so that the flow path resistance, the viscous resistance of the lubricating oil, and the like can be reduced. Thereby, compared with the structure from which the solenoid valve 17 and the injector 12 are spaced apart via piping, it is excellent in the control responsiveness. Therefore, it is suitable for a case where predetermined oiling is performed in a short time, for example, when oiling a piston ring part during piston operation.
[0063]
In the fourth embodiment of the present invention shown in FIG. 9, the branch oil supply pipe 16 is divided into a plurality of pipes 16 </ b> G on the upstream side with a solenoid valve 17 attached thereto as a boundary and a plurality of pipes with the solenoid valve 17 as a boundary. It is made up of the branched downstream branch oil supply pipe portions 16A, 16B, and 16C. The upstream piping portion 16G is connected to the common oil feeding portion 15, and an oil amount limiter 18 is attached to the piping portion 16G. Each of the downstream branch oil feeding pipe portions 16A, 16B, and 16C is individually connected to the injector. Specifically, the three downstream branch oil supply pipe portions 16A, 16B, and 16C are individually connected to and paired with the three injectors 12a to 12c attached to the half circumference portions of the cylinders 11a to 11n. The other three downstream branch oil supply pipe portions 16A, 16B, and 16C are individually connected to three injectors 12d to 12f attached to the other half-circumferential portions of the cylinders 11a to 11n. In addition, the injectors 12a to 12c and 12d to 12f may be attached alternately instead of half a circle. The configurations of the solenoid valve 17 and the oil amount limiter 18 are the same as the configurations of the solenoid valves 17a to 17c and the oil amount limiters 18a to 18n described in the first embodiment.
[0064]
The configuration other than the points described above is the same as that of the first embodiment including the portions not shown in FIG. Therefore, the fourth embodiment can obtain the same effects as the first embodiment. In addition, since lubricating oil can be distributed and supplied to a plurality of injectors through the solenoid valve 17 and lubricated to a plurality of locations, the number of solenoid valves 17 used is reduced, which is excellent in that it can be implemented at low cost.
[0065]
Next, a fifth embodiment of the present invention will be described. Since this embodiment basically has the same configuration as that of the fourth embodiment, the same components are denoted by the same reference numerals as those of the fourth embodiment, description of the configuration and operation thereof will be omitted, and different portions will be hereinafter described. explain.
[0066]
In the fifth embodiment, the length from the solenoid valve 17 to the downstream branch oil feed pipe portions 16B and 16C other than the downstream branch oil feed pipe portion 16A having the longest length among the downstream side branch oil feed pipe portions 16A to 16C. Depending on the size, the diaphragm 61 or 62 is individually attached. The flow passage cross-sectional area of the fixed throttle 62 provided in the downstream branch oil feed pipe portion 16C having the shortest pipe length is equal to the flow of the fixed throttle 61 provided in the downstream branch oil feed pipe portion 16B having the next longest pipe length. It is smaller than the road cross-sectional area.
[0067]
The configuration other than the points described above is the same as that of the fourth embodiment including portions not shown in FIG. Therefore, the same effect as the first and fourth embodiments can be obtained in the fifth embodiment. In addition, by installing the fixed throttles 61 and 62, regardless of the differences in the respective pipe lengths from the solenoid valve 17 to the plurality of injectors 12a to 12c or 12d to 12f connected thereto, The pressure loss in the pipe lines of the oil pipe portions 16A to 16C can be made uniform. For this reason, it is excellent in that it is possible to make the amount of oil injected from the injectors 12a to 12c or 12d to 12f connected to one electromagnetic valve 17 through the downstream branch oil feeding pipe portions 16A to 16C uniform. .
[0068]
  In addition, this invention is not restrict | limited to the said each embodiment. For example, in the above embodiments,The oil amount limiter is not limited to the upstream side of the electromagnetic on-off valve, and the oil amount limiter may be disposed on the downstream side. Moreover, the needle lift sensor is installed in the injector.It is possible to use the signal of the needle lift sensor for various purposes, for example, to obtain a useful signal for monitoring the lubrication situation and controlling the lubrication by detecting the lift amount of the needle with this sensor. .
[0069]
【The invention's effect】
  The present invention pumps lubricating oilAt the discharge port of the lubricant pumpA common oil feeding section for storing the lubricating oil in a pressurized state is communicated, and a plurality of branched oil feeding pipes branched from the common oil feeding section are attached to an engine cylinder so that the lubricating oil is put into the cylinder. Each injector is connected to an injector that is supplied by injection, and a normally closed electromagnetic on / off valve is attached to each of these branch oil supply pipes, and the opening timing and the open maintenance time of these electromagnetic on / off valves are individually controlled by an electronic controller. To be remotely controlled.
[0070]
  Therefore, according to the present invention, even during the operation of the engine, by changing the valve opening timing of the electromagnetic on-off valve by remote control, it is possible to lubricate the cylinder at an appropriate timing and to open the electromagnetic on-off valve. By changing the valve maintenance time by remote control, it is possible to adjust the amount of oil injected from the injector into the cylinder. Furthermore, it is possible to install the apparatus of the present invention by disposing the oil supply system of the common oil supply section and each branch oil supply pipe over the lubricating oil pump and the injector attached to each cylinder of the engine. In this case, it is not necessary to make a complicated connection using a shaft coupling, and the operation of aligning the shaft center, so that it can be easily installed in the engine.
  Furthermore, according to the present invention, an oil amount limiter is provided in each of the branch oil supply pipes, and the oil amount limiter is provided with an oil chamber, a housing having an oil inlet and an oil outlet communicating with the oil chamber, and the oil A shuttle having a throttle passage communicating the inlet and the oil outlet, and housed in the oil chamber so as to reciprocate between a first position away from the oil inlet and a second position seated on the oil inlet; And an urging body that urges the shuttle toward the first position. Therefore, according to the present invention, when the electromagnetic on-off valve breaks down and stops in the open state, the oil is moved so as to block the oil outlet of the housing by the hydraulic pressure, so that the lubricating oil is prevented from being poured in darkly. it can.
  Further, as a preferred embodiment, according to the invention in which the oil amount limiter includes a lift sensor that detects the movement of the shuttle, whether or not the shuttle is operating properly using the detection signal output from the lift sensor, for example. It is possible to know the position of the shuttle and the position of the shuttle, so that signals useful for monitoring the lubrication status and controlling lubrication can be obtained..
[0071]
Furthermore, as a preferred mode, according to the invention in which a plurality of the electromagnetic on-off valves are provided in parallel to the branch oil supply pipe, even if any of the plurality of electromagnetic on-off valves fails, other normal electromagnetic Lubrication can be ensured through the on-off valve, so the lubrication operation is highly reliable.
[0072]
Similarly, as a preferred mode, according to the invention in which the electromagnetic on-off valve is incorporated in the injector, it is suitable when predetermined lubrication is performed in a short time compared to a case where the electromagnetic on-off valve and the injector are far apart. It is.
[0073]
Similarly, as a preferred embodiment, the branch oil feed pipe has one upstream pipe section connected to the common oil feed section with the electromagnetic on-off valve as a boundary, and downstream branch feed with the electromagnetic on-off valve as a boundary. According to the invention in which the oil pipe portion is branched into a plurality of pipes and the injectors are individually connected to the downstream branch oil feed pipe portions, each electromagnetic on-off valve can lubricate to a plurality of locations via the injectors. The number of electromagnetic on-off valves used is small and can be implemented at low cost.
[0074]
Similarly, as a preferred embodiment, a throttle corresponding to the pipe length is provided in the downstream branch oil feed pipe part other than the downstream branch oil feed pipe part having the longest pipe length in the downstream branch oil feed pipe part. According to the invention, the pressure loss in each pipeline can be made uniform regardless of the difference in the length of each pipeline from the electromagnetic on-off valve to the plurality of injectors connected thereto. It is possible to make the amount of lubrication from each connected injector uniform.
[0077]
Similarly, as a preferred embodiment, according to the invention, the electronic control device controls the valve opening timing and the valve opening maintaining time on the basis of the crank angle detection signal of the engine input thereto. Since the electromagnetic on-off valve is opened and closed in synchronization with the movement of the piston operated by the engine crank, an appropriate amount of lubricating oil can be injected into the cylinder at an appropriate time.
[0078]
Similarly, as a preferred mode, according to the invention in which the electronic control device controls the valve opening maintenance time based on the engine load signal input thereto, lubrication is performed by controlling the valve opening maintenance time. Since the amount is changed, for example, as the engine load becomes higher, the valve opening maintenance time can be lengthened to increase the amount of oil to be added to the cylinder.
[0079]
Similarly, as a preferred embodiment, the electronic control device controls the valve opening maintenance time based on cylinder temperatures detected by a plurality of temperature sensors attached to the cylinder at intervals along the circumferential direction. According to the invention, the amount of lubrication can be changed by controlling the valve opening maintenance time of the electromagnetic on-off valve based on the temperature of the cylinder of the engine detected by the temperature sensor during operation. Therefore, it is possible to perform appropriate oiling according to the temperature of each part of the cylinder, such as the amount of oiling can be increased as the injector is arranged corresponding to the higher part.
[Brief description of the drawings]
FIG. 1 is a diagram showing a cylinder lubrication device according to a first embodiment of the present invention.
FIG. 2 is a diagram showing an electromagnetic on-off valve provided in the cylinder lubrication device of FIG.
3 is a time chart showing the relationship between the operation of the electromagnetic on-off valve in FIG. 2 and a crank angle signal.
4 is a cross-sectional view showing a configuration of an oil amount limiter provided in the cylinder oil supply device of FIG. 1;
FIG. 5 is a diagram showing a cylinder lubrication device according to a second embodiment of the present invention.
FIG. 6 is a diagram showing, by a hydraulic symbol, an electromagnetic on-off valve group included in the cylinder lubrication device of FIG. 2;
FIG. 7 is a diagram showing a cylinder lubrication device according to a third embodiment of the present invention.
8A is a cross-sectional view showing an example of an electromagnetic on-off valve built-in type injector provided in the cylinder lubrication device of FIG. 7; (B) is sectional drawing which shows the other example of the electromagnetic on-off valve built-in type injector with which the cylinder oil supply apparatus of FIG. 7 is provided.
FIG. 9 is a view showing a cylinder lubrication device according to a fourth embodiment of the present invention.
FIG. 10 is a view showing a cylinder lubrication device according to a fifth embodiment of the present invention.
FIG. 11 is a diagram schematically showing a configuration of a cylinder lubrication device according to a conventional example.
[Explanation of symbols]
11a to 11n ... cylinder
12, 12a-12n ... injector
13a to 13n ... temperature sensor
14 ... Lubricating oil pump
15 ... Common oil feed pipe (common oil feed section)
16, 16a to 16n ... Branch oil pipe
17, 17a-17n ... Solenoid open / close valve
18, 18a-18n ... Oil quantity limiter
19 ... Electronic control unit
20 ... Cylinder lubrication device
31 ... Housing
32 ... Shuttle
33 ... Coil spring
34 ... Oil chamber
35 ... Oil inlet
36 ... Oil outlet
36a ... Valve seat at oil outlet
37 ... Restricted passage
38 ... Lift sensor
16G: Branch oil feed pipe upstream of the branch oil feed pipe
16A, 16B, 16C ... Branch oil supply pipe downstream of the oil supply pipe
61, 62 ... Aperture

Claims (12)

An injector attached to a plurality of cylinders of the engine and injecting lubricating oil into the cylinders;
A lubricating oil pump that pumps lubricating oil;
A common oil feeding section that is provided in communication with the discharge port of the pump and stores the lubricating oil in a pressurized state; and
A plurality of branched oil supply pipes branched from the common oil supply section and connected to the injectors;
A normally closed electromagnetic on-off valve provided in each of these branch oil supply pipes;
An electronic control device for remotely controlling the valve opening timing and the valve opening maintenance time of each of these electromagnetic switching valves;
Comprising
An oil amount limiter is provided for each of the branch oil supply pipes,
The oil amount limiter has a housing having an oil chamber and an oil inlet and an oil outlet communicating with the oil chamber, a throttle passage communicating the oil inlet and the oil outlet, and is separated from the oil inlet. A shuttle housed in the oil chamber so as to be able to reciprocate over a first position and a second position seated on the oil inlet; and a biasing body that biases the shuttle toward the first position. cylinder lubricating apparatus characterized by there. The cylinder oil supply device according to claim 1, wherein the oil amount limiter includes a lift sensor that detects movement of the shuttle . The cylinder lubrication device according to claim 1, wherein the housing includes a transparent window that allows the oil chamber to be visually recognized . The said control apparatus is equipped with the shuttle determination part which determines whether the said shuttle is operate | moving appropriately based on the detection signal output from the said lift sensor, The control apparatus is characterized by the above-mentioned. Cylinder lubrication equipment. 4. The cylinder lubrication according to claim 2, wherein the control device includes a shuttle movement amount calculation unit that calculates a movement amount of the shuttle based on a detection signal output from the lift sensor. 5. apparatus. 6. The cylinder lubrication device according to claim 1, wherein a plurality of the electromagnetic on-off valves are provided in parallel to the branch oil feeding pipe . The cylinder lubrication device according to any one of claims 1 to 6, wherein the electromagnetic on-off valve is incorporated in the injector. The branch oil supply pipe has a single upstream pipe section connected to the common oil supply section with the electromagnetic on-off valve as a boundary, and a plurality of downstream branch oil supply pipe sections with the electromagnetic on-off valve as a boundary. The cylinder lubrication device according to any one of claims 1 to 6, wherein the cylinder is branched and the injector is individually connected to each of the downstream branch oil feeding pipe portions. The downstream branch oil feed pipe part other than the downstream branch oil feed pipe part having the longest pipe length in the downstream branch oil feed pipe part is provided with a restriction corresponding to the pipe length. The cylinder oiling device according to claim 8 . The electronic control device controls the valve opening timing and the valve opening maintaining time on the basis of a crank angle detection signal of the engine input to the electronic control device . The cylinder oiling device according to item 1. 10. The cylinder lubrication device according to claim 1, wherein the electronic control device controls the valve opening maintaining time based on an engine load signal input to the electronic control device. 11. . The electronic control device controls the valve opening maintenance time based on cylinder temperatures detected by a plurality of temperature sensors attached to the cylinder at intervals along a circumferential direction. The cylinder oiling device according to any one of 1 to 9.

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