JP4756846B2 - Marine speed reducer - Google Patents

Description

  The present invention relates to a marine speed reduction reversing machine.

  2. Description of the Related Art Conventionally, a marine speed reduction reverser equipped with a friction plate hydraulic clutch is known as a marine speed reduction reverser for small vessels such as motor boats and fishing boats (Patent Document 1).

  These marine speed reduction reversing machines are configured to press the friction plate by applying hydraulic pressure to the friction plate of each forward or reverse clutch and transmit the rotational speed of the output shaft to the input shaft to move forward and backward. Yes.

As means for switching the hydraulic pressure of the hydraulic clutch in accordance with the forward / rearward movement, the hydraulic oil switching valve provided in the oil passage is directly operated manually (Patent Document 1), and the electromagnetic valve is operated by an electric signal. (Patent Document 2).
Japanese Patent Laid-Open No. 6-80098 See Japanese Patent Laid-Open No. 11-182582, paragraph 0014, symbol “directly connected solenoid valve”.

  By the way, among the switching valves, the electromagnetic switching valve can be easily operated remotely, and therefore has the advantage that the ship can be maneuvered more comfortably than the manual switching valve. The function of the switching valve is likely to be impaired due to a short circuit or malfunction of the relay switch. When such a failure occurs, the spool of the solenoid valve must be directly operated by human power, so that there is a problem that maneuvering is very difficult and troublesome. On the other hand, the manually operated switching valve does not have such a problem and has an advantage that there are few failures.

  For this reason, paying attention to the respective advantages of the forward / reverse switching valve, there is a case in which a request is made to change the specification of the switching valve already installed from a manual switching valve to an electromagnetic switching valve or vice versa.

  However, the manual directional control valve and the electromagnetic directional control valve have different spool structures, and the manual directional control valve has conventionally been provided with a throttle portion for the loosely fitted valve in the valve body. If the switching valve once installed is changed from a manual switching valve to an electromagnetic switching valve or vice versa, the marine reduction / reverse gear itself, or at least The entire oil passage block to which the switching valve is attached has to be replaced, and not only the marine speed reducing reverse rotation machine and its parts are wasted at all, but also the replacement work is very troublesome. It was.

  The present invention has been made for the purpose of solving the above-described problems. Either a manual switching valve or an electromagnetic switching valve can be installed in the same hydraulic oil supply oil passage, It was made for the purpose of making it very easy to change between.

  In order to achieve the above object, a marine speed reduction reverse rotation machine according to the present invention has a structure in which the oil passage connecting surface of the forward / reverse switching valve with respect to the hydraulic oil supply oil passage has a manual switching valve in the hydraulic oil supply oil passage of the forward / reverse clutch. Both the electromagnetic switching valve and the electromagnetic switching valve are the same, and the forward / reverse switching valve of the hydraulic oil supply oil passage is replaced by either the manual switching valve or the electromagnetic switching valve by replacing the spool of the manual switching valve or the electromagnetic switching valve. It is characterized in that it can be changed.

  Further, a throttle valve for adjusting the hydraulic pressure to the loosely inserted valve may be provided in the switching valve for supplying hydraulic oil to the loosely inserted valve that adjusts the hydraulic pressure provided in the hydraulic oil supply oil passage.

In the above, the spool of the manual switching valve is a cylindrical rotating body that is received in the cylinder, and the circumferential groove corresponding to the hydraulic fluid communication opening opened at a plurality of locations in the cylinder and the circumferential groove are used as shafts. An axial groove that communicates in the direction is provided on the outer periphery, and the communication state of each opening can be selected by rotating around the shaft within the cylinder portion, and the spool of the electromagnetic switching valve is accommodated in the cylinder. A circumferential groove formed on the outer periphery of the spool through the adapter sleeve with respect to the hydraulic fluid communication opening that is slidably fitted in the adapter sleeve so as to be slidable in the axial direction. Can be configured such that the communication state of each opening of the cylinder inner surface can be selected by sliding the spool in the axial direction. .

  Further, in order to correspond to a complicated oil passage, the spool of the manual switching valve is provided with an axial through oil passage penetrating in the axial direction in the axial center portion, and either a circumferential direction or an axial groove provided on the outer periphery. The cylinder is provided with an opening that communicates with the axial penetrating oil passage, and further communicates with the axial penetrating oil passage, or an adapter sleeve of the electromagnetic switching valve is provided with an outer cylinder and an inner cylinder. The outer cylinder communicates with hydraulic fluid communication ports provided at a plurality of locations in the cylinder on the outer surface, and toward the oil passage forming step formed on the inner cylinder surface on the inner surface. An open radial through oil passage is provided, and the inner cylinder communicates with a radial through oil path opened on the inner surface of the outer cylinder and opens at a position corresponding to a circumferential groove on the outer periphery of the spool disposed inside. A radial through-hole is provided, and it is slid onto the inner cylinder. An axial penetrating oil passage penetrating in the axial direction is provided in the spool of the electromagnetic switching valve, and a radial through hole communicating with the outer peripheral surface is provided in the axial penetrating oil passage and an opening communicating with the axial through hole is provided. Can also be provided in the cylinder.

  The spool of the electromagnetic switching valve may be movable in the axial direction manually.

  A manual switching valve and an electromagnetic switching valve are provided in advance in the hydraulic oil supply oil passage as hydraulic oil forward / reverse switching valves for the friction plate portion of the forward / reverse clutch, and the manual switching valve and The electromagnetic switching valve may be arbitrarily selected.

  The operation of the loose insertion valve is controlled by a switching valve using the hydraulic pressure of the hydraulic oil supply oil passage as a pilot pressure, or the operation of the slow insertion valve is controlled by the hydraulic pressure of the hydraulic oil supply oil passage. It can also be configured to be controlled by a switching valve that operates directly.

  Further, a flow rate control throttle provided in the switching valve for controlling the operation of the loosely fitted valve is provided with a cylinder having an operating oil supply port and a discharge port on the inner surface, and an operating oil supply port on the outer periphery. It is composed of a plurality of pistons having hydraulic oil guide grooves leading to the discharge port, and the throttle amount is selected by sliding the selected pistons having different volumes of the hydraulic oil guide grooves into the cylinder. It may be adjustable. Further, in this case, the hydraulic oil guide groove is provided in a spiral shape on the outer periphery of the piston and the volume of the hydraulic oil guide groove is varied by changing the spiral length, or the sectional area of the hydraulic oil guide groove is varied. The volume of the hydraulic oil guide groove may be varied.

  According to the present invention, since the same marine speed reduction reverse gear can be easily changed to either a manual or solenoid valve switching valve simply by replacing the spool, the manual switching valve is later changed to an electromagnetic switching valve. In the case of changing the specifications, or vice versa, the spool portion can be dealt with by a so-called parts replacement operation, and the specification can be changed very easily and without waste. Even in this case, if the spool of the electromagnetic switching valve can be moved manually and the oil passage can be switched by this movement, safety in the event of failure can be ensured.

  In addition, if the control switching valve of the slow insertion valve is provided with a throttle that adjusts the hydraulic pressure to the slow insertion valve, the operation of the slow insertion valve can be performed regardless of whether it is a manual or electromagnetic switching valve without a throttle. It becomes controllable and the changeover of the switching valve becomes easier.

  If the manual switching valve and the electromagnetic switching valve are provided in the same oil passage so that the type of the switching valve can be selected by switching the oil passage, even the above parts replacement work can be omitted, and the simple oil passage The target switching valve can be used only by switching. In this case, when the electrical circuit of the electromagnetic switching valve is short-circuited or the relay switch malfunctions due to salt damage or the like, the manual switching valve also serves as a supplementary maneuvering means and has the advantage of increasing navigational safety.

  If the slow insertion valve that adjusts and controls the hydraulic pressure of the hydraulic oil supply passage is controlled by a switching valve that operates using the hydraulic pressure of the hydraulic oil passage as a pilot pressure, the hydraulic fluid for the slow insertion valve Supply can also be made directly from the pump, ensuring operation.

  Furthermore, if the loosely fitted valve is controlled by a switching valve that is directly operated by the hydraulic pressure of the hydraulic oil passage, the pilot pressure oil passage can be omitted, so that the oil passage can be simplified.

  In addition, a throttle provided in the oil passage from the hydraulic oil pump to the loose insertion valve, a cylinder having a hydraulic oil supply port and a discharge port opened on the inner surface, and an operation from the hydraulic oil supply port to the discharge port on the outer periphery If it is composed of a plurality of pistons having an oil guide groove, and the throttle amount can be adjusted by selecting and slidingly fitting the several pistons having different volumes of the hydraulic oil guide groove into the cylinder, The basic throttle amount can be easily set according to the performance of the marine speed reducer or the viscosity of the hydraulic oil. Further, as a means for adjusting the amount of restriction, the guide groove on the outer periphery of the piston is provided in a spiral shape, and the length of the hydraulic oil guide groove can be easily varied even with the same piston by changing the inclination angle of the spiral. Even with a small piston, various throttle amounts can be adjusted.

  Next, a marine speed reduction reverser that is an embodiment of the present invention will be described.

  FIG. 1 is a hydraulic circuit diagram showing a marine speed reduction reverser according to an embodiment of the present invention. A forward clutch 2f and a reverse clutch 2a are provided on an input shaft 1 that receives power from an engine (not shown).

  Although not shown in detail, the forward clutch 2f and the reverse clutch 2a are composed of friction plates and steel plates that are alternately arranged. The friction plates are connected to the inner gear, and the steel plates are always rotated. Connected to the outer gear. By pressing them with a hydraulic piston, the outer gear and the inner gear are rotated together, the large gear meshing with the inner gear is rotated, and the propeller is rotated via the propeller shaft.

  The hydraulic pistons of the forward clutch 2f and the reverse clutch 2a are supplied with the hydraulic oil switched to either the forward or backward direction from the forward oil circuit 10f or the reverse oil circuit 10a of the hydraulic oil supply oil circuit 10. It is configured.

  As shown in FIG. 1, the hydraulic oil supply oil circuit 10 includes an oil tank 3, a filter 4, a pump 5, a low speed valve 6, and a forward / reverse switching valve 7, and is fed from a low speed valve 6 capable of adjusting hydraulic pressure for low speed. The forward / reverse switching valve 7 feeds the hydraulic oil to the forward oil circuit 10f or the reverse oil circuit 10a to actuate the hydraulic piston of the forward clutch 2f or the reverse clutch 2a to transmit the propulsion rotational force of either forward or backward to the propeller. ing.

  Further, the hydraulic oil supply oil circuit 10 is provided with a loosely fitted valve 8 to prevent the forward / reverse clutches 2a, 2b from suddenly coming into contact when the forward / reverse switching valve 7 is switched. .

  This loosely fitted valve 8 is a kind of pressure regulating valve, which is fed from the pump 5 by a three-position switching valve 9 that operates using the hydraulic pressure of the forward oil circuit 10f or the reverse oil circuit 10a in the hydraulic oil supply oil circuit 10 as a pilot pressure. Hydraulic fluid to be sent is sent through the oil passage 10r.

  The three-position switching valve 9 includes a cylinder 9b and a piston 9p and a return spring 9d. When pressure oil flows into the forward oil circuit 10f or the reverse oil circuit 10a and the hydraulic pressure in the cylinder 9b increases, any one of the pistons 9p Moves, the switching valve 9 is switched, the hydraulic fluid whose flow rate is controlled by the throttle 9c flows, and is pressed into the back chamber of the loosely fitting valve 8 through the hydraulic circuit 10r, and after the switching of the forward / reverse switching valve 7, a predetermined time passes. The pressure of the relief spring is gradually increased through the control piston until the pressure reaches the pressure, that is, the set relief pressure of the slow insertion valve 8 is gradually increased so that the clutch is fully inserted at the position where the biasing force of the spring is maximized. . Further, when the hydraulic pressure is lost, the switching valve 9 is returned to the neutral state by the urging force of the return spring 9d, the flow of the hydraulic oil is stopped, and the control piston of the loose insertion valve 8 is reset to the original position.

  That is, when the forward / reverse switching valve 7 is in the neutral position (in the illustrated example), the three-position switching valve 9 is also in the neutral position, so that no pressure oil is supplied to the back chamber 8a of the loosely fitted valve 8. Yes. Therefore, at this time, the spool of the slow insertion valve 8 is largely retracted and functions as a relief valve with a low relief pressure, and a part of the pressure oil supplied from the pump 5 is ovule by the relief operation of the slow insertion valve 8. Then, the oil is released to the lubricating oil path 10L through the oil cooler 10c, and eventually circulates to the drain of the switching valve 7 through the forward / reverse clutches 2f and 2a.

  The hydraulic pressure released from the loosely fitted valve 8 to the lubricating oil path 10L is regulated to a predetermined low pressure by the lubricating hydraulic pressure setting relief valve 8b.

  Next, when the forward / reverse switching valve 7 is switched to the forward or reverse position, the three-position switching valve 9 is also moved in either the left or right direction by the piston 9p using the hydraulic pressure of the hydraulic oil starting to flow through the oil circuits 10f, 10a as a pilot pressure. When the oil passage is opened, the flow rate is controlled by the throttle 9c provided in the three-position switching valve 9, and the hydraulic oil is press-fitted into the back chamber 8a of the loosely fitted valve 8 through the hydraulic circuit 10r. As a result of this press-fitting, the spool is advanced and the relief pressure is gradually increased, the lubricating oil passage 10L is gradually closed, and as a reflective action, the operating oil pressure of the forward / reverse clutches 2f and 2a is gradually increased, and the clutch suddenly increases. It is made to prevent joining.

  Finally, the clutches 2a and 2f are completely pressed at a high pressure to completely transmit power.

  In FIG. 1, reference numeral 9c denotes a throttle provided in the three-position switching valve 9, and the flow rate of the hydraulic oil supplied to the back chamber of the loosely fitted valve 8 depends on the scale and viscosity of the marine speed reduction reverser. To be adjusted.

  Next, the forward / reverse switching valve 7 provided in the hydraulic oil supply oil circuit 10 will be described.

  A switching valve indicated by reference numeral 7a as a forward / reverse switching valve 7 in FIG. 1 indicates a manual switching valve, a switching valve indicated by reference numeral 7b indicates an electromagnetic switching valve, and can be replaced with each other as indicated by a white arrow.

  As the structure of the manual switching valve 7a is schematically shown in FIG. 2, the spool 7c is rotated by a manual handle 7d so that the forward / backward oil passage and neutral can be selected. .

  That is, the spool 7c of the manual switching valve 7a is a cylindrical rotating body, and circumferential grooves 72, 73, 74 are respectively provided at positions corresponding to the hydraulic fluid communication ports 12, 13, 14, 15 provided on the cylinder 11 side. The axial direction groove | channel 71 which is provided and connects these circumferential direction grooves in an axial direction is provided in the position connected with the adjacent circumferential direction groove | channel according to each rotation angle.

  As shown in the figure, when the manual handle 7d is neutral, for example, the hydraulic oil entering from the communication port 12 to which hydraulic oil is supplied passes from the circumferential groove 72 to the axial groove 71 and the circumferential groove 73, for example, for the drain. It flows to the communication port 15 serving as a discharge port, and the forward / reverse clutches 2f and 2a do not operate.

  When the handle 7d is tilted in the direction of arrow A so that the axial groove 71 coincides with the discharge port 13 position, the hydraulic oil entering from the communication port 12 passes through the circumferential groove 72, the axial groove 71, and the circumferential groove 73 to the other drainage. The fluid is discharged from the communication port 13 serving as an outlet, and for example, hydraulic oil flows to the forward clutch 2f to transmit the rotation in the forward direction. At this time, the drain communication port 15 is closed on the surface of the spool 7c.

  When the handle 7d is tilted in the direction of arrow B and the axial groove 71 is aligned with the position of the other communication port 14, the communication port is connected to the supply port 12 through the circumferential groove 72, the axial groove 71, and the circumferential groove 74. 14, hydraulic oil flows to the reverse clutch 2a, for example, and the rotation in the reverse direction is transmitted. At this time, the communication port 15 serving as a drain discharge port is closed by another surface of the spool 7c.

  Next, the spool 7e of the electromagnetic switching valve 7b shown in FIG. 1 is moved in the axial direction by an electromagnetic solenoid (not shown) as shown schematically in FIG. 3 for the sake of explanation. You can select forward / backward and neutral.

  That is, the spool 7e is accommodated in the adapter sleeve 75 so as to be slidable in the axial direction. This adapter sleeve 75 is a cylindrical body having the same outer diameter D as the outer shape D of the spool 7c shown in FIG. 2, and a through hole 12a communicating with the hydraulic oil communication ports 12 to 15 on the cylinder 11 side on the peripheral surface. , 13a, 14a, and 15a are provided. And the circumferential groove | channels 76 and 78 which have the axial direction width which connect each hydraulic fluid communication port 12 and 13 or hydraulic fluid communication 11 and 14 are provided in the outer peripheral surface of the spool 7e, These circumferential groove | channels 76 are provided. , 78 is provided with a circumferential groove 77 that allows the hydraulic fluid communication ports 12 and 15 to communicate in the circumferential direction. The adapter sleeve 75 is formed with an axial guide groove 15 b for communicating the communication port 15 on the cylinder 11 side with the circumferential groove 77. Further, the circumferential grooves 76 and 78 are discontinuous in the circumferential direction at the bank wall portions 76a.

  As shown in the figure, when the spool 7e is in the axial neutral position c, the hydraulic oil entering from the hydraulic oil communication port 11 is a communication port that serves as a drain outlet, for example, from the circumferential groove 77 through the axial guide groove 15b. 15a, the forward / reverse clutches 2f and 2a are not operated.

  When the spool 7e is moved in the direction A in the figure by the operation of the solenoid valve, and the circumferential groove 76 is moved so as to cover the communication port 12a and the communication port 13a, the hydraulic oil entering from the communication port 12a passes through the circumferential groove 76. The hydraulic oil is discharged from the communication port 13a and flows to the forward clutch 2f to transmit the rotation in the forward direction. At this time, the hydraulic oil is blocked by the bank walls 76a and 76a and does not flow to the communication port 14 serving as the drain outlet.

  When the spool 7e is moved in the direction B in the figure by the operation of the solenoid valve, and the circumferential groove 78 is moved so as to cover the communication port 12a and the communication port 14a, the hydraulic oil entering from the communication port 12a passes through the circumferential groove 78. The hydraulic oil is discharged from the communication port 14 and flows to the reverse clutch 2a to transmit the rotation in the reverse direction. At this time, the hydraulic oil is blocked by the bank walls 78a and 78a and does not flow to the communication port 15a serving as a drain discharge port.

  As apparent from the above, the spool 11c shown in FIG. 2 or the adapter sleeve 75 shown in FIG. 3 can be inserted into the cylinder 11 interchangeably.

  That is, when the spool 7c is inserted into the same cylinder 11, the switching valve becomes the manual switching valve 7a, and when the adapter sleeve 75 and the spool 7e are inserted, the switching valve 7b becomes the electromagnetic switching valve 7b.

  4 and 5 are cross-sectional views of a main part of a marine speed reduction reverser in which a spool 7c or 7e is attached to an actual marine speed reduction reverser.

  FIG. 4 shows the case of a manual switching valve, and FIG. 5 shows the case of an electromagnetic switching valve. However, the oil passage in an actual marine reduction reverse rotation machine is a complicated three-dimensional route, and is shown in the spool 7c and FIG. The spool 7e has an axial penetrating oil passage 79 at the axial center, which is not shown in FIGS.

  Then, the spool 7c of the manual switching valve shown in FIG. 4 is inserted into the cylinder 11, and the oil path is switched by rotating around the shaft while supporting the handle 7d, so that the hydraulic oil is transferred to the forward clutch 10f or the reverse clutch 10a. Guided.

  The openings corresponding to the communication ports 12 to 15 shown in FIG. 2 are indicated by w, x, y, z in FIG. 4, and the respective openings w, through the circumferential grooves 72, 73, 74 and the axial groove 71 are shown. The oil path is switched to x, y, and z.

  Reference numeral 9 denotes a switching valve for hydraulic oil with respect to the loosely fitted valve 8, and is operated with the hydraulic pressure of the oil passages 10f, 10a shown in FIG. 1 as pilot pressure. Reference numeral 90 denotes a piston constituting a throttle, which has circumferential grooves 94 and 95 on the outer periphery thereof and an axial groove 96 that communicates them, and the piston 90 resists the elastic force of the spring 95 by the hydraulic pressure applied to the switching valve 9. Is moved in the cylinder 93 to the left in the figure, the oil passage openings 91, 92 provided in the cylinder 93 and the circumferential grooves 94, 95 are in communication with each other. The flow rate is controlled by the axial groove 96, and this hydraulic oil is guided to the back chamber 8a of the loosely fitted valve 8 as shown by a dotted line.

  Next, the spool 7e of the electromagnetic switching valve 7b shown in FIG. 5 will be described.

  In FIG. 5, reference numeral 80 denotes an electromagnetic solenoid, and 80a denotes a wiring connector to a controller (not shown). In the figure, reference numeral 81 denotes a spindle of the electromagnetic solenoid 80, which is connected to the spool 7e by a pin 81a. The other end 82 of the spindle 81 protrudes from the electromagnetic solenoid 80 and can be moved in the axial direction by being pushed in the direction of the arrow, and can also be operated manually.

The adapter sleeve 75 that houses the spool 7e is composed of an outer cylinder 75a and an inner cylinder 75b, and three-dimensionally forms an oil passage from each opening 12-15 in the cylinder 11 to the circumferential groove of the spool 7e. Have been to.
That is, the outer cylinder 75a communicates with the openings w, x, y, and z on the inner surface of the cylinder 11 on the outer surface, and radially passes through the inner surface toward the oil passage forming step 75c on the surface of the inner cylinder 75b. An oil passage 75r is provided, and the inner cylinder 75b communicates with a radial penetrating oil path 75r opened on the inner surface of the outer cylinder 75a and opens in a position corresponding to a circumferential groove on the outer periphery of the spool disposed inside. A hole 75q is provided, and the oil path is switched to the respective openings w, x, y, z by causing the electromagnetic solenoid 80 to move the spindle 81 in and out in the left-right direction in the figure.

  As apparent from the above, the spool 7c or the adapter sleeve 75 and the spool 7e can all be inserted and installed in the same cylinder 11, and can be manually inserted or fixed by inserting and fixing one of them. Has been to function as.

That is, as shown in FIG. 6, the spool 7e can be selectively inserted into the cylinder 11 via the spool 7c or the adapter sleeve 75 as indicated by an arrow, and functions as a switching valve no matter which one is mounted. Has been.
In addition, as shown in FIG. 7, the manual switching valve 7a and the electromagnetic switching valve 7b are replaced with the same hydraulic oil supply oil as the forward / backward switching valve for the hydraulic oil for the forward / reverse clutches 2f and 2a as shown in FIG. These switching valves 7a and 7b are provided in parallel in the circuit 10 and are switched by a switching valve 41 interposed in the hydraulic oil passages 10a and 10f between the switching valves 7a and 7b and the forward and backward clutches 2f and 2a. You may make it get.

  FIG. 8 shows an external perspective view when the manual switching valve 7a and the electromagnetic switching valve 7b are provided together with the marine deceleration reverser 20. This marine speed reduction reverser 20 includes a mounting flange portion 21 connected to a flywheel casing portion provided on an output rotation shaft of an engine, a gear case portion 22 containing forward and backward clutches 2a, 2f, gears, and the like, and hydraulic oil supply. An external appearance including an oil passage case portion 23 containing an oil passage is provided, and a casing 24a containing a manual switching valve 7a in the oil passage case portion 23 and a casing 24b containing an electromagnetic switching valve 7b are provided side by side. An oil passage switching valve is provided on the back side of the drawing.

  In this case, the manual switching valve 7a and the electromagnetic switching valve 7b can be switched immediately by switching the switching valve 41 (FIG. 7).

  In the hydraulic oil supply oil circuit 10 shown above, as the control valve 9 for sending hydraulic oil to the loosely fitted valve 8, the three positions are operated using the hydraulic pressure of the hydraulic oil passages 10f and 10a as pilot pressure as shown in FIG. In addition to the switching valve 9, as shown in FIG. 9, a two-position switching valve 9a that operates with the cylinder 9b and two pistons 9p arranged in series using the hydraulic pressure of the hydraulic oil passages 10f and 10a as a pilot pressure may be used. As shown in FIG. 10, the oil pressure of the forward oil passage 10f and the reverse oil passage 10a may be directly used as the operating oil pressure, and the two-position switching valve 9a may be operated by the cylinder 9b and the two pistons 9p arranged in series.

  In this case, since the pistons 9p and 9p housed in the cylinder 9b are directly driven by the hydraulic oil, a pilot hydraulic circuit is not necessary.

  In any case, the switching valves 9, 9a are provided with a throttle 9c. Accordingly, it is not necessary to provide a throttle portion in the forward / reverse switching valve 7 portion, and the switching of the switching valve to the manual type or the electromagnetic type can be easily performed by replacing only the spool portion of the valve.

  FIGS. 11A to 11C are perspective views of the valve body 90 of the throttle 9c shown in FIG. 4 or FIG. The valve body 90 is in the form of a piston that is slidably fitted into a cylinder 93 having a hydraulic oil inlet 91 and an outlet 92 as indicated by dotted lines in the figure. On the outer periphery of the valve body 90, circumferential grooves 94 and 95 are provided at positions corresponding to the hydraulic oil inlet 91 and the outlet 92, and the circumferential grooves 94 and 95 are communicated by a spiral groove 96. ing. A plurality of valve bodies 90 (three in the illustrated example, a to c) are provided for the cylinder 93, and the length of the spiral groove 96 is as shown in FIGS. 9 (a) to 9 (c). By making the lead angle g of the spiral different, it is made different for each valve body 90. The difference in oil amount is determined by this difference.

  Note that the amount of restriction can be adjusted by changing the cross-sectional area of the spiral groove having the same lead angle g in addition to the spiral length. If the spiral groove is used in this way, the amount of change in the amount of restriction can be easily widened even with a piston-like valve body having a short axial length.

  As described above, the forward / reverse switching valve of the marine reduction / reversal reverse gear according to the present invention can be easily exchanged from a manual switching valve to an electromagnetic switching valve or vice versa by so-called parts replacement work of the spool portion. Since the restriction of hydraulic oil to the valve is provided in the switching valve portion other than the forward / reverse switching valve, it is possible to easily replace either the manual or electromagnetic switching valve.

  In addition, if the throttle structure has a spiral groove on the outer periphery of the piston and the flow rate is controlled by the flow path resistance of this spiral groove, the length can be shortened by changing the lead angle of the spiral groove 96. Even if the piston has a short axial length, the flow rate can be controlled in a wide range.

It is an oil circuit diagram of the hydraulic-oil supply oil path of the marine reduction reverse rotation machine which is embodiment of this invention. It is a typical perspective view for demonstrating the manual switching valve which is embodiment of this invention. It is a typical perspective view for demonstrating the electromagnetic switching valve which is embodiment of this invention. It is principal part sectional drawing which attached the manual switching valve to the marine deceleration reverse rotation machine which is embodiment of this invention. It is principal part sectional drawing which attached the electromagnetic switching valve to the marine reduction reverse rotation machine which is embodiment of this invention. It is a principal part exploded sectional view which wrote together the manual switching valve and electromagnetic switching valve which are attached to the marine reduction reverse rotation machine which is embodiment of this invention. It is an oil circuit diagram which shows the other structural example of the hydraulic-oil supply oil path which is embodiment of this invention. It is an external appearance perspective view of the marine speed reduction reverser which has the oil circuit shown in FIG. It is an oil circuit diagram which shows the further another structural example of the hydraulic-oil supply oil path which is embodiment of this invention. It is an oil circuit diagram which shows the further another structural example of the hydraulic-oil supply oil path which is embodiment of this invention. It is a perspective view which shows the structure of the aperture | diaphragm | squeeze part used for the hydraulic-oil supply oil path which is embodiment of this invention, (a) is a thing with a short spiral groove, (b) is an intermediate thing, (c) is the longest. The thing is shown.

Explanation of symbols

1 Input shaft 2f Forward clutch 2a Reverse clutch 3 Oil tank 4 Filter 5 Oil pump 6 Low speed valve 7 Forward / reverse switching valve 7a Manual switching valve 7b Electromagnetic switching valve 7c Manual switching valve spool 7e Electromagnetic switching valve spool 8 Slow fitting valve 8a Back chamber 9 of loosely inserted valve Hydraulic oil switching three-position switching valve 9a to the loosely inserted valve Hydraulic oil switching two-position switching valve 10 to the loosely inserted valve Hydraulic oil supply oil circuit 10L Lubricating oil path 10f Forward oil circuit 10a For reverse Oil circuit 11 Cylinder 12 Hydraulic oil communication port 13 Hydraulic oil communication port 14 Hydraulic oil communication port 15 Hydraulic oil communication port 75 Adapter sleeve 75a Outer cylinder 75b Inner cylinder 80 Electromagnetic solenoid

Claims (13)

  In the hydraulic oil supply oil passage of the forward / reverse clutch, the structure of the oil passage connection surface of the forward / reverse switching valve with respect to the hydraulic oil supply oil passage is the same for both the manual switching valve and the electromagnetic switching valve, and the hydraulic oil supply oil passage The marine reduction / reverse gear is characterized in that the forward / reverse switching valve can be changed to either a manual switching valve or an electromagnetic switching valve by exchanging the spool of the manual switching valve or the electromagnetic switching valve.   The marine speed reduction reverser according to claim 1, wherein a throttle valve for adjusting hydraulic pressure of hydraulic oil for the loosely inserted valve is provided in a switching valve for supplying hydraulic oil to the loosely inserted valve provided in the hydraulic oil supply oil passage. The spool of the manual switching valve is a cylindrical rotating body that is received in the cylinder, and a circumferential groove corresponding to a hydraulic fluid communication opening opened at a plurality of locations in the cylinder and the circumferential groove in the axial direction. An axial groove for communication is provided on the outer periphery, and the state of communication of the respective openings can be selected by rotating around the shaft within the cylinder portion, while the spool of the electromagnetic switching valve is fitted in the cylinder. A circumferential groove formed on the outer periphery of the spool via the adapter sleeve is slidably fitted in the adapter sleeve so as to be slidable in the axial direction and opened to a plurality of locations in the cylinder via the adapter sleeve. It is constituted so that it may communicate, and it is constituted so that the communicating state of each opening of the cylinder inner surface can be selected by sliding the spool in the axial direction. Marine reverse and reduction gear according to claim 1 or 2.   The spool of the manual switching valve has an axial through oil passage in an axial center portion, and either the circumferential direction provided on the outer periphery or the axial groove communicates with the axial through oil passage, and the axial direction The marine speed reduction reverser according to any one of claims 1 to 3, wherein an opening communicating with the through oil passage is provided in the cylinder.   The adapter sleeve of the electromagnetic switching valve has a double structure of an outer cylinder and an inner cylinder, and the outer cylinder communicates with hydraulic fluid communication ports provided at a plurality of locations in the cylinder on the outer surface, and the inner surface Is provided with a radially penetrating oil passage that opens toward an oil passage forming step formed on the surface of the inner cylinder, and the inner cylinder communicates with a radially penetrating oil passage that opens on the inner surface of the outer cylinder. The marine speed reduction reverser according to any one of claims 1 to 4, wherein a radial through hole is provided at a position corresponding to a circumferential groove on the outer periphery of the spool disposed inside.   The spool of the electromagnetic switching valve is provided with an axial through oil passage penetrating in the axial direction in an axial center portion, and at least one circumferential groove on the outer periphery communicates with the axial through oil passage, and the axial penetration is provided. The marine speed reduction reverser according to any one of claims 1 to 5, wherein an opening communicating with the oil passage is provided in the cylinder.   A manual switching valve and an electromagnetic switching valve are provided in advance in the hydraulic oil supply oil passage as a forward / reverse switching valve for the hydraulic oil of the forward / backward clutch, and the manual switching valve and the electromagnetic switching valve are provided in parallel by the hydraulic passage switching valve. The marine speed reduction reverse gear according to any one of claims 1 to 6, wherein the marine speed reduction reverse gear can be arbitrarily selected.   The marine speed reduction reverser according to any one of claims 1 to 7, wherein the spool of the electromagnetic switching valve can be moved in the axial direction also manually, and the oil path can be switched by this movement.   The marine reduction reverse gear according to any one of claims 1 to 8, wherein the operation of the loosely fitted valve is controlled by a switching valve that operates using the hydraulic pressure of the hydraulic oil supply oil passage as a pilot pressure.   The marine reduction reverse gear according to any one of claims 1 to 8, wherein the operation of the loosely fitted valve is controlled by a switching valve that is directly operated by the hydraulic pressure of the hydraulic oil supply oil passage.   A flow control throttle provided in the switching valve for controlling the operation of the loosely inserted valve includes a cylinder having a hydraulic oil supply port and a discharge port opened on the inner surface, and the hydraulic oil supply port to the discharge port on the outer periphery. It is composed of a plurality of pistons having hydraulic oil guide grooves, and the throttle amount can be adjusted by selecting and slidingly fitting the several pistons having different volumes of the hydraulic oil guide grooves into the cylinder. The marine speed reduction reverser according to any one of claims 1 to 10.   The marine speed reduction reverse gear according to claim 11, wherein the hydraulic oil guide groove is provided in a spiral shape on the outer periphery of the piston, and the volume of the hydraulic oil guide groove is varied by changing the helical length.   The marine speed reduction reversing machine according to claim 11 or 12, wherein the volume of the hydraulic oil guide groove is made different by changing the cross-sectional area of the hydraulic oil guide groove.

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