JP2012035718A - Sealing device of rotary vane type helm machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a sealing device of a rotary type vane helm machine which can maintain sealing effect, and can quickly and surely sense breakage of a seal from the outside even when no oil pressure exists in a working fluid chamber for extracting oil pressure for sealing, when oil pressure becomes negative and when the wear of a sealing surface occurs.SOLUTION: A branch line 51a is provided to a control hydraulic line 9i from a discharge port in a control hydraulic pump 9g to a solenoid pilot valve 9c for controlling a directional selector valve 9b. A control hydraulic adjusting valve 51b and sealing oil spill valve 51c are arranged in series in the branch line 51a. An outlet line of the sealing oil spill valve is connected to a tank return oil line. A sealing hydraulic line 51e is branched from an intermediate line situated between the control oil pressure adjusting valve and sealing oil spill valve, and the sealing hydraulic 51e is connected to a sealing oil inflow port 13a in an impact-proof valve block 10.

Description

  The present invention relates to a rotary vane type steering machine, which is a type of ship steering machine, and to a sealing device therefor.

  A conventional rotary vane type steering machine has a housing 1 and a rotor 2 housed therein, as shown in FIGS. In the rotor 2, a lower shaft portion 2 a is supported by a boss portion 1 a provided at the bottom of the housing 1, and an upper shaft portion 2 b is supported by an annular top cover 3 disposed in the upper opening of the housing 1. A radial bearing 4a and a thrust bearing 4b are inserted between the boss portion 1a and the lower shaft portion 2a, and a radial bearing 4c is inserted between the top cover 3 and the upper shaft portion 2b. 2 is rotatably held inside the housing 1 fixed to the hull in a state where a load is applied in the radial direction and the axial direction.

  The rotor 2 has an internal through-hole 2c into which a rudder shaft (not shown) is inserted, and a plurality of vanes 2d are projected at equal intervals along the circumferential direction of the outer peripheral surface. The housing 1 is provided with the same number of segments 1b as the vanes 2d protruding at equal intervals along the circumferential direction of the inner peripheral surface.

  Each vane 2d of the rotor 2 holds an upper horizontal seal 2f slidably contacting the lower surface of the top cover 3 in an upper horizontal slit 2e formed on the upper end surface, and a housing 1 in a lower horizontal slit 2g formed on the lower end surface. A lower horizontal seal 2h that is in sliding contact with the inner bottom surface of the housing 1 is held, and a vertical seal 2j that is in sliding contact with the inner peripheral surface of the housing 1 is held in a vertical slit 2i formed on the distal end surface in the radial direction. In addition, the segment 1b of the housing 1 holds a vertical seal 1d that is in sliding contact with the outer peripheral surface of the rotor 2 in a vertical slit 1c formed on the distal end surface in the radial direction. Each of the seals 2f, 2h, 2j, 1d is made of an elastic material.

  In the rotor 2, the upper and lower horizontal seals 2f and 2h are in sliding contact with the back surface of the top cover 3 and the inner bottom surface of the housing 1, respectively, and the vertical seal 2i is in sliding contact with the inner peripheral surface of the housing 1 in the housing 1. The vertical seal 1d rotates while being in sliding contact with the outer peripheral surface of the rotor 2, whereby hydraulic oil chambers 5a, 5b, 5c, and 5d are formed between the vane 2d and the segment 1b.

  The top cover 3 holds an annular upper ring seal 3b having an integral structure in an upper ring slit 3a formed at a portion facing the upper end surface 2k of the rotor 2. The housing 1 holds an integrally formed annular lower ring seal 1f in a lower ring slit 1e formed at a portion facing the lower end surface 2l of the rotor 2. The upper and lower ring seals 3b and 1f are each made of an elastic material, the ring seal surface 3c of the upper ring seal 3b contacts the upper end surface 2k of the rotor 2, and the ring seal surface 1g of the lower ring seal 1f is the rotor 2 In contact with the lower end face 21 of each, sealing action is performed.

  Due to the upper and lower ring seals 3b and 1f, the hydraulic oil in each of the hydraulic oil chambers 5a to 5d allows the minute gap between the upper end surface 2k of the rotor 2 and the top cover 3 and the lower end surface 2l of the rotor 2 and the housing 1 to move. Leakage (or leakage) to the adjacent hydraulic oil chambers 5a to 5d and the rotor shaft portions 2a and 2b communicating with the atmosphere through the minute gap between the inner bottom surface is prevented.

  Further, the outer peripheral edge 3d of the ring seal of the upper ring seal 3b is in contact with the inner peripheral upper end edge 2n of the upper horizontal seal 2f of the vane 2d and the inner peripheral upper end edge 1h of the vertical seal 1d of the segment 1b. The outer peripheral edge 1i of the ring seal 1f is in contact with the inner peripheral lower end edge 2o of the lower horizontal seal 2h of the vane 2d and the inner peripheral lower end edge 1j of the vertical seal 1d of the segment 1b, whereby the upper portion of the vane 2d The hydraulic fluid passes through the upper and lower inner peripheral edge portions 2n and 2o of the lower horizontal seals 2f and 2h and the upper and lower inner peripheral edge portions 1h and 1j of the vertical seal 1d of the segment 1b. Leakage from (5a, 5c or 5b, 5d) to the adjacent low-pressure side hydraulic oil chamber (5b, 5d or 5a, 5c) is prevented.

  The rotor 2 is provided with a balance hole 2m that communicates the upper end surface 2k inside the position of the upper ring seal 3b and the lower end surface 2l inside the position of the lower ring seal 1f. If pressure oil leaks from the upper and lower ring seals 3b and 1f, the pressure acting on the upper end surface 2k and the lower end surface 2l of the rotor 2 is balanced in the vertical direction via the balance hole 2m. It is supposed to be. As a result, uneven force due to the differential pressure in the axial direction is prevented from being generated in the rotor 2.

The hydraulic oil chambers 5a and 5c and the hydraulic oil chambers 5b and 5d that are at positions opposite to the rotation axis of the rotor 2 are in communication with each other. For example, pressure oil is supplied from the hydraulic pump to the hydraulic oil chamber 5a. When supplied, pressure oil is simultaneously supplied to the hydraulic oil chamber 5c at the counter electrode, while oil is simultaneously discharged from the remaining hydraulic oil chambers 5b and 5d and returned to the hydraulic pump side.
Thereby, rotation of the rotor 2 by pressure oil is materialized.

  In order to ensure the oil tightness of the hydraulic oil chambers 5a to 5d, the upper and lower horizontal seals 2f and 2h of the vane 2d, the vertical seal 2j, the vertical seal 1d of the segment 1b, and the upper and lower ring seals 3b and 1f Apply pressure oil from the hydraulic oil chamber (5a, 5c or 5b, 5d) on the high-pressure side to each back surface opposite to the seal surface that contacts and slide, and press the seal surface against the mating surface ing.

  That is, FIG. 8 shows a cross-sectional shape of the horizontal seals 2f and 2h and the vertical seals 1d and 2j, and FIG. 9 shows a cross-sectional shape of the ring seals 3b and 1f. As shown in FIGS. 8 and 9, each of the seals 1d, 1f, 2f, 2h, 2j, and 3b is on the opposite side of the seal surfaces 1g, 1k, 2p, 2q, 2r, and 3c that are in sliding contact with each other. By causing the pressure oil guided from the hydraulic oil chambers 5a to 5d to act on the rear surfaces 1m, 1n, 2s, 2t, 2u, and 3e, the seal surfaces 1g, 1k, 2p, 2q, 2r, and 3c are slid on the other side. It is pressed against the surface to give sealing properties.

  The seals 1d, 1f, 2f, 2h, 2j, and 3b have skirt portions 1o, 1p, 2v, 2w, 2x, and 3f on the back surfaces 1m, 1n, 2s, 2t, 2u, and 3e, respectively. . The pressure oil simultaneously acts on the skirt portions 1o, 1p, 2v, 2w, 2x, and 3f, and the skirt portions 1o, 1p, 2v, 2w, 2x, and 3f are connected to the slits 1c and 1e. , 2e, 2g, 2i, 3a. This prevents the pressure oil from leaking to the low pressure side through the gaps between the slits 1c, 1e, 2e, 2g, 2i, 3a and the seals 1d, 1f, 2f, 2h, 2j, 3b. Yes.

  Further, the connecting portions of the upper and lower horizontal seals 2f, 2h and the vertical seal 2j of the vane 2d are configured as shown in FIGS. 10 to 13 show the connecting portion between the upper horizontal seal 2f and the upper side of the vertical seal 2j, and the connecting portion between the lower horizontal seal 2h and the lower side of the vertical seal 2j is symmetrical to this. It is configured. The horizontal seal 2f lacks the skirt portion 2v at the connecting portion with the vertical seal 2j, and the upper end portion of the vertical seal 2j is fitted into this missing portion. Thus, in the state where the upper and lower horizontal seals 2f, 2h and the vertical seal 2j are mounted in the slits 2e, 2g, 2i, respectively, the space of the rear surfaces 2s, 2t of the upper and lower horizontal seals 2f, 2h and the vertical seal 2j The hydraulic fluid guided to the back surface 2u of the vertical seal 2j also acts on the back surfaces 2s and 2t of the upper and lower horizontal seals 2f and 2h.

  Thus, in order to prevent the high-pressure hydraulic fluid from leaking to the low-pressure side through between the respective end surfaces of the upper and lower horizontal seals 2f, 2h and the vertical seal 2j and the mating surfaces, these seals 2f, 2h. , 2j in the respective slits 2e, 2g, 2i, the respective seals 2f, 2h, 2j are given a slight elastic compression in the longitudinal direction. Contact surface pressure is generated on each end face of 2f, 2h, 2j. Further, in order to prevent leakage of high-pressure hydraulic oil through the respective contact surfaces between the end surfaces of the skirt portions 2v and 2w of the upper and lower lateral seals 2f and 2h and the skirt portion 2x of the vertical seal 2j, these contacts are prevented. A contact surface pressure is generated by elastic compression when the surface is mounted in the slits 2e, 2g, 2i.

  Further, regarding the vertical seal 2j of the vane 2d and the vertical seal 1d of the segment 1b in which the linear lengths of the seal surfaces 2r and 1k are generally longer, the hydraulic oil guided from the hydraulic oil chambers 5a to 5d to the back surfaces 2u and 1m, respectively. As shown in FIGS. 11 and 14, the back surface 2u and the vertical slit 2i of the vertical seal 2j of the vane 2d are provided so that the seal surface pressure is applied to the seal surfaces 2r and 1k even when the pressure is low or zero. 15 and 16, as shown in FIGS. 15 and 16, in the space between the back surface 1m of the vertical seal 1d of the segment 1b and the vertical slit 1c, corrugated springs 7 each having the following role are respectively provided. Intervened in a free state.

  In other words, while the ship is navigating straight with the rudder in a neutral state, the rudder is always operated at a small rudder angle to correct the course of the ship from shifting due to disturbance. The generated hydraulic pressure is low, and therefore a sufficient force for pressing the back surfaces 2u and 1m of the vertical seals 2j and 1d cannot be given. The corrugated leaf spring 7 is for applying a necessary minimum surface pressure to the seal surfaces 2r and 1k even if sufficient hydraulic pressure is not generated.

  The space between the back surface 2u of the vertical seal 2j and the vertical slit 2i and the space between the back surface 1m of the vertical seal 1d and the vertical slit 1c are very narrow, and can be inserted into these narrow spaces. In order to give a long spring force (pressing force) to the vertical seals 1d and 2j, it is necessary to use the corrugated spring 7 having a large spring constant.

  In the conventional structure of the upper and lower ring seals 1f and 3b, as shown in FIG. 9, the ring seals 1f and 3b are pushed in the radial direction by the hydraulic pressure acting on the outer peripheral edges 1i and 3d, so that the ring seal 1f , 3b and the hydraulic oil chamber (5a, 5c or 5b, 5d on the high pressure side) because no positive countermeasure is taken against the occurrence of a gap allowing leakage between the outer peripheral side surface of the slits 1e and 3a. ) Instead of acting only on the rear surfaces 1n and 3e of the ring seals 1f and 3b, first, the hydraulic oil is guided to the inner peripheral side surface and further guided to the rear surfaces 1n and 3e. The thing which made it carry out the sealing in an outer peripheral surface with the sealing in 3c is also disclosed (for example, refer the following patent document 1).

The means for guiding the pressure oil from the hydraulic oil chambers 5a to 5d to the back surfaces 1m, 1n, 2s, 2t, 2u and 3e of the respective seals 1d, 1f, 2f, 2h, 2j and 3b are as follows.
First, as means for guiding pressure oil from the hydraulic oil chamber (5a, 5c or 5b, 5d) on the high pressure side to the vertical seal 2j of each vane 2d and the back surfaces 2s, 2t, 2u of the upper and lower horizontal seals 2f, 2h. Since the vane 2d is a rotating body, as shown in FIG. 14, each of the two hydraulic oil chambers 5a, 5d and the adjacent hydraulic oil chambers 5b, 5c communicate with each vane 2d. The chamber communication holes 2y are provided, the pressure valves 6 are attached to the respective oil chamber communication holes 2y, and the vane 2d is provided with a working hole 2z leading from the outlet hole 6c of the pressure valve 6 to the back surface 2u of the vertical seal 2j. At the same time, the back surfaces 2s and 2t of the upper and lower horizontal seals 2f and 2h communicate with the back surface 2u of the vertical seal 2j through connecting portions with the vertical seal 2j. Accordingly, the hydraulic pressure acting on the back surface 2u of the vertical seal 2j simultaneously acts on the back surfaces 2s and 2t of the upper and lower horizontal seals 2f and 2h.

  As shown in FIG. 14, the pressure valve 6 has a valve seat 6d screwed into both inlets 6b of the valve main body 6a, and two ball valve bodies 6e are allowed to move freely between the two valve seats 6d. A spring 6f is interposed between the ball valve bodies 6e, and an outlet hole 6c is provided so as to communicate with the pressure valve inlet 6b with the ball valve body 6e opened from the valve seat 6d. The screw portion 6g is cut and an O-ring 6h is provided on the outer diameter portion at the other end. The pressure valve 6 is mounted in the oil chamber communication hole 2y by tapping one end portion of the oil chamber communication hole 2y and screwing the screw portion 6g of the valve body 6a into the tap.

  Thus, for example, when the hydraulic oil chamber 5a is on the high pressure side and the hydraulic oil chamber 5d is on the low pressure side, the hydraulic pressure in the high pressure side hydraulic oil chamber 5a opens one ball valve body 6e of the pressure valve 6 and The ball valve body 6e is pressed against the valve seat 6d to perform a non-return action, thereby preventing the high-pressure side hydraulic oil chamber 5a from communicating with the low-pressure side hydraulic oil chamber 5d, and the high-pressure side pressure oil acting. It acts on the back surface 2u of the vertical seal 2j through the hole 2z. Conversely, when the hydraulic oil chamber 5d is on the high pressure side and the hydraulic oil chamber 5a is on the low pressure side, the hydraulic oil in the hydraulic oil chamber 5d acts on the back surface 2u of the vertical seal 2j by the reverse operation.

  Next, regarding the vertical seal 1d of the segment 1b, instead of applying hydraulic pressure to the back surface 1m, the high pressure oil in the hydraulic oil chambers 5a to 5d is directly guided to the sealing lip portion to perform the sealing action. (For example, see Patent Document 1 below). In this case, it is not necessary to provide means for guiding the pressure oil from the hydraulic oil chamber on the high pressure side to the back surface 1m of the vertical seal 1d of the segment 1b.

  However, when the vertical seal 1d of the segment 1b has the same structure as the vertical seal 2j of the vane 2d, as shown in FIG. 15, the vertical seal 1d from the hydraulic oil chamber (any one of 5a to 5d) on the high pressure side. Pressure oil is led to the back 1m of the. That is, similarly to the case of the vane 2d of the rotor 2, the segment 1b is provided with an oil chamber communication hole that connects the adjacent hydraulic oil chambers 5a and 5b and the adjacent hydraulic oil chambers 5c and 5d, respectively, A pressure valve 6 is provided in the communication hole.

  Next, as shown in FIGS. 5 and 16, for the upper and lower ring seals 3b and 1f, there is an oil passage 3g that leads from the upper end of the back 1m of the vertical seal 1d of the segment 1b to the back 3e of the upper ring seal 3b. An oil passage 1q that is perforated in the top cover 3 and communicates from the lower end portion of the back surface 1m of the vertical seal 1d to the back surface 1n of the lower ring seal 1f is perforated in the bottom portion of the housing 1, thereby providing a high-pressure side. Pressure oil from the hydraulic oil chambers 5a to 5d is applied to the back surfaces 3e and 1n of the upper and lower ring seals 3b and 1f.

  In the following Patent Document 1, in the case of Claims 3 and 4 and Claims 6 and 7, since the pressure oil from the hydraulic oil chamber on the high pressure side is not introduced into the vertical seal of the segment, the upper and lower ring seals As a means for introducing the pressure oil from the hydraulic oil chamber on the high pressure side, for example, the outlet of the pressure valve provided in the vane is connected to the balance hole penetrating the rotor up and down in the same claim. The upper and lower openings of the upper and lower ring seals are respectively communicated with the inner peripheral side surface.

In order to supply hydraulic oil to the hydraulic oil chambers 5a to 5d of the rotary vane type steering machine configured as described above, one of the hydraulic circuits shown in FIG. 17 or FIG. 18 is provided.
The hydraulic circuit shown in FIG. 17 is a case where a control hydraulic pump 9g is provided. The hydraulic circuit shown in FIG. 18 is a case where the control hydraulic pump 9g is not provided. As shown in FIG. 17 or FIG. 18, the hydraulic circuit includes, as main components, a hydraulic pump 9a having a one-way constant discharge amount, a direction switching valve 9b, and an electromagnetic pilot valve 9c for controlling the direction switching valve 9b. A pilot check valve 9d, a flow rate adjusting valve 9e, and an oil tank 9f are provided.

  The direction switching valve 9b performs path switching for switching the supply destination of the discharge oil from the hydraulic pump 9a to one of the hydraulic oil chambers 5a and 5c and the hydraulic oil chambers 5b and 5d, and operates to the hydraulic oil chambers 5a to 5d. When oil is not supplied, it has a function of switching to the neutral position and returning the oil discharged from the hydraulic pump 9a to the oil tank 9f as it is. In addition, the pilot check valve 9d allows the hydraulic oil to enter the hydraulic oil chambers 5a to 5d when the hydraulic oil is not supplied from the hydraulic pump 9a to the hydraulic oil chambers 5a and 5c or the hydraulic oil chambers 5b and 5d. Confine and fix the rudder. The flow rate adjusting valve 9e adjusts the flow rate so that the operation of the pilot check valve 9d is not shocking.

  In the case of using the hydraulic circuit shown in FIG. 17, the control hydraulic pressure necessary for operating the direction switching valve 9b is supplied from the control hydraulic pump 9g provided coaxially with the hydraulic pump 9a through the control hydraulic line 9i. The

  In the case where the hydraulic circuit shown in FIG. 18 is used, the control hydraulic pressure necessary for operating the direction switching valve 9b uses the discharge hydraulic pressure of the hydraulic pump 9a as the control hydraulic pressure for the direction switching valve 9b. In this case, even if the steering gear is in a no-load or low-load state, or the direction switching valve 9b is in the neutral position and the oil discharged from the hydraulic pump 9a is returned to the oil tank 9f as it is, A pressure regulating valve 9h is provided in the return oil line 9L from the direction switching valve 9b to the oil tank 9f so that the discharge hydraulic pressure of the hydraulic pump 9a is maintained at a predetermined value or more, and the hydraulic line at the inlet of the pressure regulating valve 9h is The regulation hydraulic line 9j is regulated to a constant pressure by the pressure regulating valve 9h, and the sealing hydraulic line 9k is branched from the regulation hydraulic line 9j.

Further, when an abnormally large impact load is applied to the rudder, in order to prevent the impact load from damaging the steering machine, as shown in FIGS. One oil passage 3h communicating with 5a, 5c and the other oil passage 3i communicating with the hydraulic oil chambers 5b, 5d are provided through. On the upper surface of the top cover 3, an impulse valve block 8 having inflow / outflow holes 8a and 8b communicating with the oil passages 3h and 3i, respectively, is attached.
The anti-shock valve block 8 includes one anti-shock valve 8c that causes one inflow / outlet hole 8a to flow into the other outflow / inflow hole 8b, and one outflow / inflow hole that uses the other outflow / inflow hole 8b as the inflow side. The other anti-shock valve 8d that flows out to 8a is internally provided.

  When an abnormally large impact load acts on the rudder and, for example, the hydraulic pressure on the side of the hydraulic oil chambers 5a and 5c rises abnormally, one of the shock-proof valves 8c operates through the oil passage 3h and the outflow inlet 8a, The oil in the hydraulic oil chambers 5a and 5c escapes to the hydraulic oil chambers 5b and 5d through the outflow / inflow holes 8b and the oil passage 3i, and the impact load is reduced. Conversely, when an abnormal hydraulic pressure is generated on the hydraulic oil chambers 5b, 5d side, the other anti-shock valve 8d is opened in the same manner, and the oil in the hydraulic oil chambers 5b, 5d is transferred to the hydraulic oil chambers 5a, 5c. Run to the side.

  In addition, Patent Document 2 is known to use a means different from the above for the sealing oil system of the seal. In Patent Document 2, oil chamber communication holes 2y are provided in the rotor vane 2d and the housing segment 1b, respectively, and pressure valves 6 are provided in the full chamber communication holes 2y, respectively, so that the hydraulic oil from the hydraulic oil chamber on the high pressure side is sealed. Rather than by means of guiding to the back of the hydraulic oil, the hydraulic oil that has become the high-pressure side is extracted as the sealing hydraulic pressure from the respective inlet lines of the anti-shock valves 8c, 8d communicating with the hydraulic oil chambers 5a, 5b, 5c, 5d. , Lead it to the back of each seal.

  In order to give the minimum pressing force necessary for the seal surface of each seal even when the load on the steering gear is small and no hydraulic pressure is generated in the hydraulic oil in the hydraulic oil chambers 5a, 5b, 5c, 5d, the rotor When the control hydraulic pump 9g is provided instead of the means of providing the corrugated spring 7 on the back of the vertical seal 2j of the vane 2d and the vertical seal 1d of the housing segment 1b, the hydraulic pressure from the control hydraulic line 9i or When the control hydraulic pump is not provided, the sealing hydraulic pressure line is obtained by extracting the hydraulic pressure from the specified hydraulic pressure line 9j for obtaining the control hydraulic pressure from the main hydraulic pressure line from the respective inlet lines of the above-described anti-impact valves 8c and 8d. By connecting to, the corrugated leaf spring 7 is made unnecessary.

  In this case, the sealing hydraulic pressure is extracted from the respective inlet lines of the anti-shock valves 8c, 8d, and is extracted from the vertical seal 2j of the rotor vane 2d, the vertical seal 1d of the housing segment 1b, the upper ring seal 3d, and the lower ring seal f1. Means for guiding the respective back surfaces 2u, 1m, 3e, and 1n are as follows.

  An anti-shock valve block 10 is provided on the top surface of the top cover 3, and as shown in FIGS. 19 to 21, the anti-shock valve block 10 is formed with one outflow / inflow hole 10a and the other outflow / inflow hole 10b. The one outflow / inflow hole 10a communicates with one oil passage 3h formed in the top cover 3, and the other outflow / inflow hole 10b communicates with the other oil passage 3i formed in the top cover 3. . The one oil passage 3h communicates with the first group of hydraulic oil chambers 5a and 5c, and the other oil passage 3i communicates with the second group of hydraulic oil chambers 5b and 5d.

  Also, the anti-shock valves 8c and 8d are mounted in the anti-shock valve block 10, and the one inflow / outlet hole 10a is provided on the inflow side of one anti-shock valve 8c and the outflow side of the other anti-shock valve 8d. The other inflow / outflow hole 10b communicates with the inflow side of the other anti-shock valve 8d and the outflow side of one of the anti-shock valves 8c.

  Thus, if an abnormally large impact load acts on the rudder and, for example, an abnormally high hydraulic pressure is generated in the hydraulic oil chambers 5a and 5c, the hydraulic pressure is supplied from the hydraulic oil chambers 5a and 5c to one of the oil passages 3h and the other. The one of the anti-shock valves 8c is operated through the inflow / outflow hole 10a, the one of the anti-shock valves 8c is discharged to the other outflow / inflow hole 10b, and the other oil passage 3i is operated on the low pressure side. Escape to the oil chambers 5b and 5d. Thereby, the impact load concerning a steering machine is relieve | moderated. Conversely, if an abnormally high hydraulic pressure is generated on the hydraulic oil chambers 5b and 5d side, the hydraulic pressure passes through the other oil passage 3i and the other inflow / outlet hole 10b from the hydraulic oil chambers 5b and 5d. The shock prevention valve 8d is operated, flows out from the other shock prevention valve 8d to one inflow / outflow hole 10a, escapes to the hydraulic oil chambers 5a and 5c on the low pressure side through one oil passage 3h. Thereby, the impact load concerning a steering machine is relieve | moderated.

  Further, one branch oil passage 10c is provided in one outflow / inflow hole 10a of the above-described anti-impact valve block 10, and a rising oil passage 10e is provided from a terminal portion of the branch oil passage 10c, and one reverse oil passage is provided at an end portion thereof. The inlet of the stop valve 10g is connected. Also, the other branch oil passage 10d is provided in the other outflow / inflow hole 10b, the rising oil passage 10f is provided from the end portion of the branch oil passage 10d, and the inlet of the other check valve 10h is connected to the end portion thereof. is doing. Further, in the impulse valve block 10, the outlet of one check valve 10g and the outlet of the other check valve 10h are communicated with each other through a communication oil passage 10i. Further, the communication oil passage 10i and the impulse valve block 10 are connected. A pressure oil extraction port 10k formed on the lower surface of the oil is communicated with a block-side oil supply passage 10j.

  As shown in FIGS. 21 and 22, an annular upper ring groove 11 a is provided on the upper end surface 2 k of the rotor 2, and the upper ring groove 11 a and the pressure oil extraction port 10 k of the impulse valve block 10 communicate with each other. Then, a cover-side oil supply passage 12 a is drilled in the top cover 3. Thus, the communication oil passage 10i and the upper ring groove 11a communicate with each other via the block side and cover side oil supply passages 10j and 12a and the pressure oil extraction port 10k. The upper ring groove 11 a communicates with the upper end of the balance hole 2 m of the rotor 2 and also communicates with the inner peripheral edge of the upper ring slit 3 a provided in the top cover 3.

  As shown in FIG. 23, an annular lower ring groove 11c is provided on the lower end surface 21 of the rotor 2, and the lower ring groove 11c communicates with the lower end of the balance hole 2m of the rotor 2 and The lower ring slit 1e provided on the inner bottom surface also communicates with the inner circumferential edge.

  Further, as shown in FIG. 24, a sealing oil hole 11b is formed through the main body of the rotor 2 and the vane 2d. The upper end opening of the sealing oil hole 11b communicates with the upper ring groove 11a, and the other end opening communicates with the bottom surface of the vertical slit 2i of the vane 2d.

Further, as shown in FIGS. 20 to 21, the anti-shock valve block 10 is provided with sealing oil introducing means.
The sealing oil introduction means includes a sealing oil inlet 13a, a sealing oil check valve 13b, a sealing oil passage 13c, and a sealing oil communication oil passage 13d. That is, the sealing oil inflow port 13 a is provided on one side surface of the anti-shock valve block 10, and the sealing oil check valve 13 b is provided on the other side surface of the anti-shock valve block 10. The sealing oil passage 13c is provided from the sealing oil inlet 13a to the inlet (inflow) side of the sealing oil check valve 13b. The sealing oil communication oil passage 13d is provided in communication with the outlet (outflow) side of the sealing oil check valve 13b and the other end of the communication oil passage 10i.

  As described above, the sealing oil guided to the upper ring groove 11a communicates with the inner peripheral edge of the upper ring slit 3a provided in the top cover 3, as shown in FIG. It acts on the back surface 3e of the upper ring seal 3b through the inner peripheral side surface of the ring seal 3b.

  The sealing oil guided to the back surface 3e of the upper ring seal 3b further acts on the back surface 1m of the vertical seal 1d of the housing segment 1b through the oil hole 3j provided in the top cover 3.

  Further, as shown in FIGS. 22 to 23, the sealing oil guided from the upper ring groove lla to the lower ring groove llc through the balance hole 2 m of the rotor 2 is contained in the lower ring slit 1 e provided in the housing 1. It also communicates with the peripheral edge, and acts on the back surface 1n of the lower ring seal 1f through the inner peripheral side surface of the lower ring seal 1f.

JP2003-161371 JP2008-037187

  In the above conventional type, since the vane 2d is a moving body, pressure oil is supplied from the hydraulic oil chamber (5a, 5c or 5b, 5d) on the high-pressure side to the rear surfaces 2s of the seals 2f, 2h, 2j of the vane 2d. , 2t, 2u, the pressure valve 6 must be used as shown in FIG. However, when the high pressure hydraulic oil presses the ball valve body 6e against the valve seat 6d to perform a check action, the action gives an impact to the valve main body 6a of the pressure valve 6, and the pressure valve 6 is repeated. 6 is screwed into the oil chamber communication hole 2y, and the screw valve 6g is loosened. Finally, the pressure valve 6 is dropped from the oil chamber communication hole 2y into the hydraulic oil chambers 5a to 5d. There was a problem of being inoperable. Moreover, since the drop of the pressure valve 6 is in the hydraulic oil chambers 5a to 5d, there is a problem that the drop cannot be confirmed unless the steering gear is disassembled and opened.

  Further, the space between the outlet hole 6c and the action hole 2z of the pressure valve 6 and the back surface 2u of the vertical seal 2j of the rotor vane 2d is the check action of both ball valve bodies 6e and the sealing of the skirt portion 2x of the vertical seal 2j. Because of the small volume space closed by the action, the hydraulic oil chambers 5a, 5b, 5c, and 5d that have become high pressure (particularly hydraulic oil that has become high pressure due to impact load) are closed. Therefore, a high surface pressure that is severe for the seal surface 2r tends to be constantly applied to the seal surface 2r of the vertical seal 2j. For this reason, on the seal surface 2r, there is a problem that formation of a lubricating oil film is hindered, friction is increased, and wear is easily promoted.

  Further, the pressure oil is introduced from the hydraulic oil chamber (5a, 5c or 5b, 5d) on the high pressure side to the respective back surfaces 1m, 1n, 2s, 2u, 3e of the respective seals 1d, 1f, 2f, 2h, 2j, 3b. Thus, each sealing surface 1g, 1k, 2p, 2q, 2r, 3c is pressed against the mating surface to provide sealing properties. However, when the steering gear is unloaded or lightly loaded, the hydraulic oil chamber ( 5a, 5c or 5b, 5d) does not generate sufficient hydraulic pressure, so that the pressing force generated on each sealing surface 1g, 1k, 2p, 2q, 2r, 3c is insufficient and sufficient sealing performance cannot be obtained. There is a problem that the hydraulic oil in the hydraulic oil chambers 5a to 5d is likely to leak. Accordingly, the predetermined angular position at which the rudder is commanded cannot be maintained, and a so-called creeping phenomenon occurs and the rudder flows. Then, the steering device operates so as to correct the amount of flow of the rudder by the follower. Thus, in order to keep the rudder in place, the steerer must continually repeat the corrective action, which is undesirable from the standpoint of operation and wear.

  In order to alleviate this problem, the back surface of each of the vertical seals 2j and 1d with respect to the vertical seal 2j of the vane 2d and the vertical seal 1d of the segment 1b, which are greatly affected by the long linear length of the sealing. Even if the corrugated springs 7 are inserted into the spaces between 1 m and 2 u and the slits 1 c and 2 i, respectively, even if sufficient hydraulic pressure is not generated in the hydraulic oil chambers 5 a to 5 d, the repulsion of the corrugated springs 7. An initial surface pressure is applied to each of the seal surfaces 1k and 2r by force.

  However, when the seal surfaces 1k and 2r of the vertical seals 1d and 2j are worn, the distance between the back surfaces 1m and 2u of the vertical seals 2j and 1d and the slits 1c and 2i increases, and the corrugated spring 7 Spring force (pressing force) decreases. In particular, since the wave spring 7 having a large spring constant is used, the degree of decrease in the spring force of the wave spring 7 with respect to the increase in the interval is large. Therefore, as the wear of the seal surfaces 1k and 2r of the vertical seals 1d and 2j progresses, the spring force of the corrugated spring 7 rapidly decreases, the pressing force pressing the seal surfaces 1k and 2r against the mating surface becomes insufficient, and the hydraulic oil There is a problem that the sealing effect of the vertical seals 1d, 2j by the corrugated spring 7 is reduced when sufficient hydraulic pressure is not generated in the chamber (5a, 5c or 5b, 5d). As a result, the amount of hydraulic oil leakage between the hydraulic oil chambers increases, and the steering machine must frequently repeat the steering angle correction operation.

  Further, when the corrugated spring 7 is inserted into the space between the back surfaces 1m and 2u of the vertical seals 2j and 1d and the slits 1c and 2i, it is difficult to fix the corrugated spring 7 in the space. Yes, the corrugated spring 7 is mounted in a free state and holds its position by the spring force. Therefore, when the seal surfaces 1k and 2r of the vertical seals 1d and 2j are worn, the position holding by the spring force is weakened, the position of the corrugated leaf spring 7 is changed, and the contact of the seal surfaces 1k and 2r becomes uneven. There are problems such as variations in sealing performance and uneven wear of the seal surfaces 1k and 2r.

  Further, since the vertical seal 2j of the vane 2d, the upper and lower horizontal seals 2f and 2h, the vertical seal 1d of the segment 1b, and the upper and lower ring seals 3b and 1f are each made of a resin rubber material, The additive contained may cause a chemical change in composition and become brittle and break. In this case, there is a problem that it is difficult to quickly and surely detect from the outside that the respective seals 1d, 1f, 2f, 2h, 2j, and 3b are damaged.

  Further, in Patent Document 2, the minimum pressing force necessary for the seal surface of each seal is provided even when the load on the steering gear is small and no hydraulic pressure is generated in the hydraulic oil in the hydraulic oil chambers 5a, 5b, 5c, and 5d. For this purpose, the hydraulic pressure guided to the back of each seal is the same as the hydraulic pressure for control.

Conventionally, the necessary minimum pressing force of the sealing surface provided by the corrugated spring 7 is generally 1 to ² kg / cm ² , whereas the hydraulic pressure required for control is generally 5 to 10 kg / cm ^2. It is.

  Accordingly, a pressing force that greatly exceeds the required pressing force always acts on the seal surface. This hinders formation of a lubricating oil film on the seal surface, increases the friction of the seal surface, and tends to promote wear of the seal surface.

  The present invention extracts the sealing hydraulic pressure while eliminating the need to install a pressure valve for extracting the sealing sealing hydraulic pressure from the hydraulic oil chamber and a corrugated spring on the back of the seal that gives the minimum pressing force to the sealing surface. Even if there is no hydraulic pressure in the hydraulic fluid chamber, or when the pressure becomes negative, or even when the seal surface is worn, the seal surface will not always exceed the minimum required level. A sealing device for a rotary vane type steering machine that can maintain a stable sealing effect by applying a pressing force and that can quickly and surely detect the failure of the seal when the seal is broken. The purpose is to provide.

In order to achieve the above object, a sealing device for a rotary vane type steering machine according to the present invention includes a rotor fitted and mounted on a rudder shaft, and a housing that houses the rotor and forms a space for an oil chamber around the rotor. And an annular top cover disposed in the upper opening of the housing, and a plurality of vanes are disposed at equal intervals along the circumferential direction of the outer peripheral surface of the rotor, and along the circumferential direction of the inner peripheral surface of the housing A plurality of segments are arranged at equidistant positions, and the oil chamber space is divided into a plurality of hydraulic oil chambers by vanes and segments. The first group of hydraulic oil chambers to be rotated to the left and the second group of hydraulic oil chambers to be rotated in the left and right directions. Each rotor vane includes a back surface of the top cover and a housing. Longitudinal and transverse slits are formed in the radial front end surface and the top and bottom end surfaces so as to face the inner peripheral surface and inner bottom surface of the housing, and a vertical seal that is in sliding contact with the inner peripheral surface of the housing is inserted into the vertical slit. Then, an upper horizontal seal that is in sliding contact with the back surface of the top cover is inserted into the upper horizontal slit, a lower horizontal seal that is in sliding contact with the inner bottom surface of the housing is inserted into the lower horizontal slit, and each of the seals is formed of an elastic material. The back surface of the vertical seal is communicated with the back surfaces of the upper and lower horizontal seals, pressure oil is applied to the back surface of the vertical seal so as to apply a contact surface pressure to the sliding surface, and one of the fluids communicated with the first group of hydraulic oil chambers. An outflow / inflow hole, the other outflow / inflow hole communicating with the hydraulic oil chamber of the second group, and one anti-shock valve that discharges the pressure oil flowing from one outflow / inflow hole to the other outflow / inflow hole when an impact is applied And the pressure flowing in from the other outlet / inlet The A rotary vane steering gear that anti 衝弁 blocks are disposed with a another anti 衝弁 flowing into one inflow and outflow hole,
The top cover holds an annular upper ring seal in an upper ring slit formed in a portion facing the upper end surface of the rotor, and the housing is in a lower ring slit formed in a portion facing the lower end surface of the rotor. And the rotor has a balance hole communicating with the upper end surface radially inward of the upper ring seal and the lower end surface radially inward of the lower ring seal. An inlet of one check valve is connected to one branch oil passage branched from the outflow / inflow hole, and an inlet of the other check valve is connected to the other branch oil passage branched from the other outflow / inflow hole. A communication oil passage that communicates the outlet of the stop valve is provided in the anti-shock valve block, and an oil supply passage that connects the communication oil passage of the anti-shock valve block and the annular upper ring groove provided on the upper end surface of the rotor. A sealing oil hole is provided through the vane from the rotor. The sealing oil hole is provided between the shock valve block and the top cover, and communicates with the upper ring groove and the bottom surface of the vertical slit of the vane. The upper ring groove is formed on the upper ring seal. The hydraulic pump communicates with the inner peripheral side surface and the rear surface, communicates with the inner peripheral side surface and the rear surface of the lower ring seal through the balance hole, and discharges from the hydraulic pump to the hydraulic circuit that supplies the hydraulic oil to the hydraulic oil chamber. A directional control valve for switching the supply destination of the hydraulic fluid to one of the hydraulic oil chamber of the first group and the hydraulic oil chamber of the second group, and a control hydraulic pressure for controlling switching of the directional switching valve from a control hydraulic pressure line A control hydraulic pump for supplying to the electromagnetic pilot valve of the direction switching valve is provided, and the sealing valve block is provided with a sealing oil inlet, a sealing oil check valve, Rotary vane type provided with a sealing oil passage communicating with the oil inlet and the inlet side of the sealing oil check valve, and a sealing oil communication oil passage communicating with the outlet side of the sealing oil check valve and the communication oil passage In the steering machine,
A branch line is provided in the control hydraulic line from the discharge port of the control hydraulic pump to the electromagnetic pilot valve that controls the direction switching valve, and the control hydraulic pressure adjusting valve and the sealing oil spill valve are provided in series in the branch line. The outlet line was connected to the tank return oil line, the sealing hydraulic line was branched from the intermediate line between the control hydraulic pressure adjustment valve and the sealing oil spill valve, and the sealing hydraulic line was connected to the sealing oil inlet of the anti-shock valve block It is characterized by that.

  In the sealing device for a rotary vane type steering machine of the present invention, a branch line is provided in a control hydraulic line from the discharge port of the control hydraulic pump to an electromagnetic pilot valve that controls the direction switching valve, and the first control hydraulic pressure is provided in the branch line. The adjusting valve and the second control hydraulic pressure adjusting valve are provided in parallel, the first control hydraulic pressure adjusting valve and the sealing oil spill valve are provided in series, the outlet line of the sealing oil spill valve is connected to the tank return oil line, (1) The sealing hydraulic line is branched from the intermediate line between the control hydraulic pressure adjusting valve and the sealing oil spill valve, and the outlet line of the second controlled hydraulic pressure adjusting valve is connected to the tank return oil line to detect the loss of the sealing hydraulic pressure. Is provided on the inlet side of the first control hydraulic pressure adjustment valve and the second control hydraulic pressure adjustment valve so as to switch the first control hydraulic pressure adjustment valve to the second control hydraulic pressure adjustment valve. It is characterized in.

Furthermore, the sealing device of the rotary vane type steering machine of the present invention includes a rotor fitted to and mounted on the rudder shaft, a housing that houses the rotor and forms an oil chamber space around the rotor, and an upper opening of the housing. A plurality of vanes arranged at equally spaced positions along the circumferential direction of the outer circumferential surface of the rotor, and plural at equal spaced positions along the circumferential direction of the inner circumferential surface of the housing. The oil chamber space is divided into a plurality of hydraulic oil chambers by vanes and segments, and the plurality of hydraulic oil chambers rotate the rotor in one direction left and right by the supplied pressure oil. The hydraulic oil chamber and the second group of hydraulic oil chambers that rotate in the left and right directions are divided into two groups. Each rotor vane has a back surface of the top cover, an inner peripheral surface and an inner bottom surface of the housing. Vertical and horizontal slits are formed on the radial front end surface and the upper and lower end surfaces so as to face each other, and a vertical seal that is in sliding contact with the inner peripheral surface of the housing is inserted into the vertical slit, and the top horizontal slit is Insert the upper horizontal seal that is in sliding contact with the back of the cover, insert the lower horizontal seal that is in sliding contact with the inner bottom surface of the housing into the lower horizontal slit, and form each of the above seals with an elastic material. One inflow / outlet hole communicating with the back surface of the horizontal seal, pressure oil acting on the back surface of the vertical seal so as to apply a contact surface pressure to the sliding surface, and communicating with the first group of hydraulic oil chambers; The other outflow / inlet hole communicating with the hydraulic oil chamber, the one anti-shock valve that flows the pressure oil flowing in from the one outflow / inflow hole at the time of impact load into the other outflow / inflow hole, and the other outflow / inflow hole Compressed oil into one outlet / inlet A rotary vane steering gear that anti 衝弁 blocks are disposed with a another anti 衝弁 the output,
The top cover holds an annular upper ring seal in an upper ring slit formed in a portion facing the upper end surface of the rotor, and the housing is in a lower ring slit formed in a portion facing the lower end surface of the rotor. And the rotor has a balance hole communicating with the upper end surface radially inward of the upper ring seal and the lower end surface radially inward of the lower ring seal. An inlet of one check valve is connected to one branch oil passage branched from the outflow / inflow hole, and an inlet of the other check valve is connected to the other branch oil passage branched from the other outflow / inflow hole. A communication oil passage that communicates the outlet of the stop valve is provided in the anti-shock valve block, and an oil supply passage that connects the communication oil passage of the anti-shock valve block and the annular upper ring groove provided on the upper end surface of the rotor. A sealing oil hole is provided through the vane from the rotor. The sealing oil hole is provided between the shock valve block and the top cover, and communicates with the upper ring groove and the bottom surface of the vertical slit of the vane. The upper ring groove is formed on the upper ring seal. The hydraulic pump communicates with the inner peripheral side surface and the rear surface, communicates with the inner peripheral side surface and the rear surface of the lower ring seal through the balance hole, and discharges from the hydraulic pump to the hydraulic circuit that supplies the hydraulic oil to the hydraulic oil chamber. There is provided a direction switching valve for switching the supply destination of the hydraulic oil to either the first group of hydraulic oil chambers or the second group of hydraulic oil chambers, and a return oil line from the direction switching valve to the oil tank. The control hydraulic pressure for controlling the switching of the direction switching valve is supplied from the discharge port side of the hydraulic pump to the electromagnetic pilot valve of the direction switching valve, and the pressure is applied to the return oil line. A valve is provided, and the above-described anti-shock valve block includes a sealing oil inlet, a sealing oil check valve, a sealing oil passage communicating with the sealing oil inlet and the inlet side of the sealing oil check valve, and a sealing oil reverse In the rotary vane type steering machine provided with the sealing oil communication oil passage communicating with the outlet side of the stop valve and the communication oil passage,
A control hydraulic pressure adjustment valve and a sealing oil spill valve are provided in series in the return oil line from the direction switching valve to the oil tank. ・ The sealing hydraulic line is connected from the return oil line between the control hydraulic pressure adjustment valve and the sealing oil spill valve. It is branched and the sealing hydraulic line is connected to the sealing oil inlet of the anti-shock valve block.

  Moreover, in the sealing device for a rotary vane type steering machine of the present invention, a first control hydraulic pressure adjustment valve and a sealing oil spill valve are provided in series on the return oil line from the direction switching valve to the oil tank, and the first control hydraulic pressure adjustment is performed. The sealing hydraulic line is branched from the return oil line between the valve and the sealing oil spill valve, the sealing hydraulic line is connected to the sealing oil inlet of the anti-shock valve block, and the second in parallel with the first control hydraulic pressure adjusting valve. A control hydraulic pressure adjustment valve is provided, the outlet line of the second control hydraulic pressure adjustment valve is connected to the tank return oil line, and the first control hydraulic pressure adjustment valve is switched to the second control hydraulic pressure adjustment valve by detecting the loss of the sealing hydraulic pressure. The switching valve is provided on the inlet side of the first control hydraulic pressure adjustment valve and the second control hydraulic pressure adjustment valve.

  According to the rotary vane type steering machine of the present invention, the sealing branched from the control oil line or branched from the return oil line from the hydraulic oil direction switching valve to the oil tank and led to the back of each seal Since the oil always overflows from the sealing oil spill valve to the oil tank, the seal surface is lower than the control hydraulic pressure, as defined by the pressure adjusting action of the sealing oil spill valve. It is possible to apply a sealing oil maintained at a hydraulic pressure that can provide a predetermined and constant pressing force that does not exceed the necessary minimum.

  Therefore, even if the hydraulic oil extracted as the hydraulic pressure for sealing from the hydraulic oil chamber, which is provided in parallel with the sealing hydraulic line, no longer exists due to no load, or the hydraulic oil pressure in the hydraulic oil chamber is negative. Even when the pressure is increased, a predetermined and minimum necessary pressing force can be applied to the seal surface to maintain a stable sealing effect. In that case, the pressing force against the sealing surface does not exceed the minimum pressing force necessary. Thus, the friction and wear of the sealing surface is minimized. Furthermore, even when the seal surface is worn, the effect is always constant, unlike the case of the corrugated spring.

  Furthermore, the space behind the seal is not a closed space with a small volume, as is the case with conventional pressure valves. For this reason, the high pressure hydraulic oil does not always act on the back surface of the seal due to pressure accumulation, and the lubricating oil film on the sealing surface is not destroyed, and the friction and wear of the sealing surface are not promoted by the destruction of the lubricating oil film. . Further, since the pressure valve can be eliminated, it is possible to eliminate the possibility that the pressure valve will drop into the machine.

  Also, the sealing oil that branches off from the control oil line or branched from the return oil line of the hydraulic oil from the direction switching valve to the oil tank, led to the back of each seal, When the hydraulic pressure is lost due to damage to the oil tank due to damage to the oil tank, the switching valve that detects the loss of the hydraulic pressure shuts off the line of the first control hydraulic control valve and the sealing oil spill valve for creating the sealing oil At the same time, the control hydraulic pressure is switched to the second control hydraulic pressure adjusting valve line only for creating the control hydraulic pressure, so that the control hydraulic pressure at a predetermined height is ensured even in the event of loss of the sealing hydraulic pressure due to damage to the seal. I can do it.

  Further, it is possible to detect from the outside that an abnormality such as breakage has occurred in the seal when the switching valve is switched to the position of the second control hydraulic pressure adjusting valve.

Hydraulic circuit diagram of the sealing device of the rotary vane type steering machine in the first embodiment of the present invention Hydraulic circuit diagram of the sealing device of the rotary vane type steering machine in the second embodiment of the present invention Hydraulic circuit diagram of the sealing device of the rotary vane type steering machine in the third embodiment of the present invention Hydraulic circuit diagram of the sealing device of the rotary vane type steering machine in the fourth embodiment of the present invention It is a whole longitudinal cross-sectional view of the conventional rotary vane type steering machine, and is a longitudinal cross-sectional view taken along the line aa in FIG. Same bird's-eye view of partial cross section of rotary vane steering gear Same horizontal cross section of the rotary vane type steering machine Horizontal sectional view in the free state of the vertical and horizontal seals of the rotor vane and the vertical seal of the housing segment of the rotary vane type steering machine Same as above, vertical sectional view of ring seal of rotary vane type steering machine in free state The perspective view of the vane which shows the connection part of the top horizontal seal and vertical seal of a rotor vane of a rotary vane type steering machine Bb arrow sectional view in FIG. Cc arrow sectional view in FIG. Dd arrow sectional view in FIG. Horizontal sectional view explaining the supply of sealing oil by the pressure valve to the vertical seal of the rotor vane of the rotary vane type steering machine Horizontal sectional view explaining supply of sealing oil by pressure valve to vertical seal of housing segment of rotary vane type steering machine Same as above, detailed enlarged vertical sectional view of section C in FIG. 5 of the rotary vane type steering machine Hydraulic circuit diagram when the control hydraulic pump of the rotary vane type steering machine is provided Hydraulic circuit diagram without the hydraulic pump for controlling the rotary vane type steering machine It is a longitudinal cross-sectional view of the anti-vibration valve block of a rotary vane type steering machine, and is a cross-sectional view taken along line ee in FIG. Same as above, top view of anti-shock valve block of rotary vane type steering machine It is a longitudinal cross-sectional view of the anti-vibration valve block of a rotary vane type steering machine, and is a cross-sectional view taken along line ff in FIG. A longitudinal sectional view for explaining the supply of sealing oil to the upper ring seal and the housing segment vertical seal of the rotary vane type steering machine The longitudinal cross-sectional view explaining supply of sealing oil to the lower ring seal of a rotary vane type steering machine A longitudinal sectional view for explaining the supply of sealing oil to the vertical seal of the rotor vane of the rotary vane type steering machine

  A first embodiment of the present invention will be described below with reference to FIG. Note that members that perform basically the same operations as those of the conventional members described above with reference to FIGS. The same applies to the following description of the second to fourth embodiments.

  As shown in FIG. 1, the control hydraulic pressure required to operate the direction switching valve 9b for switching the direction of the hydraulic oil applied to the hydraulic oil chambers 5a to 5d of the rotary vane type steering machine is coaxial with the hydraulic pump 9a. Is supplied through a control hydraulic line 9i and an electromagnetic pilot valve 9c from a control hydraulic pump 9g. A branch line 51a is branched from the control hydraulic line 9i, and a control hydraulic pressure adjusting valve 51b and a sealing oil spill valve 51c are provided in series on the branch line 51a. The outlet line of the sealing oil spill valve 51c is connected to the return oil line 9L to the oil tank. The sealing hydraulic line 51e is branched from an intermediate line 51d between the control hydraulic pressure adjusting valve 51b and the sealing oil spill valve 51c in the branch line 51a, and the sealing hydraulic line 51e is connected to the sealing oil inlet 13a of the anti-shock valve block 10. .

  The hydraulic pressure level of the control hydraulic line 9i is defined by the resistance with which oil in the control hydraulic line 9i relieves to the oil tank 9f through the control hydraulic pressure adjusting valve 51b and the sealing oil spill valve 51c. The hydraulic pressure of the sealing hydraulic line 51e is defined by the resistance with which oil in the sealing hydraulic line 51e relieves to the oil tank 9f through the sealing oil spill valve 51c.

  Therefore, the resistance provided in the sealing oil spill valve 51c is to relieve the oil in the sealing hydraulic line 51e to the oil tank 9f so that the oil in the sealing hydraulic line 51e becomes the minimum oil pressure necessary for sealing the seal. It is the size that gives the quantity. Further, the resistance provided in the control hydraulic pressure adjusting valve 51b is a control hydraulic pressure line such that the oil in the control hydraulic pressure line 9i becomes a necessary hydraulic pressure for controlling the direction switching valve 9b together with the resistance of the sealing oil spill valve 51c. This is a size that gives a relief amount of 9i oil to the oil tank 9f.

  The discharge amount of the control hydraulic pump 9g is the amount of oil necessary to operate the direction switching valve 9b and the amount of oil that always overflows from the control hydraulic pressure adjustment valve 51b and the sealing oil spill valve 51c to the oil tank 9f. Total amount.

Hereinafter, the operation and effect of the above-described configuration will be described.
As shown in FIG. 1, the oil discharged from the control hydraulic pump 9g passes through the electromagnetic pilot valve 9c, reaches the direction switching valve 9b, and passes from the intermediate line 51d of the branch line 51a through the sealing check valve 13b. It reaches the back of each seal.

  Thus, since the space behind each seal is a closed space, there is no oil flow in the sealing hydraulic line 51e, and when the direction switching valve 9b is in the neutral position, the electromagnetic pilot valve 9c There is no oil flow in the control hydraulic line 9i. Accordingly, the total amount of oil discharged from the control hydraulic pump 9g overflows from the branch line 51a to the oil tank 9f through the control hydraulic pressure adjustment valve 51b and the sealing oil spill valve 51c.

In this state, the hydraulic pressure of the sealing hydraulic line 51e becomes a hydraulic pressure defined by the resistance of the sealing oil spill valve 51c. This hydraulic pressure is provided in parallel with the sealing hydraulic pressure line 51e, even when the hydraulic oil extracted as the hydraulic pressure for sealing from the hydraulic oil chambers 5a to 5d no longer exists due to no load, Even when the oil pressure in the oil chambers 5a to 5d becomes a negative pressure, it is a height at which a predetermined and minimum necessary pressing force can be applied to the sealing surface, and generally varies depending on the sealing conditions. / Cm ² . And the height of this hydraulic pressure will not be exceeded in any change in the operating state.

Further, the hydraulic pressure of the control hydraulic pressure line 9i becomes a hydraulic pressure defined by the resistance of the control hydraulic pressure adjusting valve 51b and the sealing oil spill valve 51c. The hydraulic pressure is generally 5 to 10 kg / cm ^{2 although} it varies depending on the conditions of the control device.
Effect Even when the hydraulic oil extracted as the hydraulic pressure for sealing from the hydraulic oil chambers 5a to 5d provided in parallel with the sealing hydraulic pressure line 51e is no longer present due to no load, Even when the hydraulic pressure becomes negative, a predetermined minimum necessary pressing force can be applied to the seal surface to maintain a stable sealing effect. In that case, the pressing force against the sealing surface does not exceed the minimum pressing force necessary. Thus, the friction and wear of the sealing surface is minimized. Furthermore, even when the sealing surface is worn, the effect is always constant, unlike the case of the corrugated spring 7.

  Further, the space behind the seal is not a closed space with a small volume as in the case of the conventional pressure valve 6. For this reason, the high pressure hydraulic oil does not always act on the back surface of the seal due to pressure accumulation, and the lubricating oil film on the sealing surface is not destroyed, and the friction and wear of the sealing surface are not promoted by the destruction of the lubricating oil film. .

Moreover, since the pressure valve 6 can be eliminated, it is possible to eliminate the possibility that it will drop into the machine.
Next, a second embodiment of the present invention will be described with reference to FIG. In this embodiment, the control hydraulic pressure required for operating the direction switching valve 9b for switching the direction of the hydraulic oil applied to the hydraulic oil chambers 5a to 5d and the sealing hydraulic pressure required for sealing the seal are the first Instead of providing a control hydraulic pump 9g as in the embodiment and supplying from it, it is configured to be obtained by the following means.

  That is, as shown in FIG. 2, a control hydraulic pressure adjusting valve 52a and a sealing oil spill valve 52b are provided in series on a specified hydraulic line 9j from which hydraulic oil discharged from the hydraulic pump 9a exits the direction switching valve 9b, and sealing is performed. The outlet line of the oil spill valve 52b is connected to the return oil line 9L to the hydraulic oil tank 9f. A sealing hydraulic line 52d is branched from an intermediate line 52c between the control hydraulic pressure adjusting valve 52a and the sealing oil spill valve 52b, and the sealing hydraulic line 52d is connected to the sealing oil inlet 13a of the anti-shock valve block 10. A control hydraulic line 52e is branched from the discharge line of the hydraulic pump 9a, and this line 52e is guided to the direction switching valve 9b via the electromagnetic pilot valve 9c.

  The minimum hydraulic pressure is set as the discharge hydraulic pressure of the hydraulic pump 9a by the following means, and it becomes the control hydraulic pressure through the control hydraulic pressure line 52e. That is, in the line through which the hydraulic oil discharged from the hydraulic pump 9a passes through the specified hydraulic line 9j exiting the direction switching valve 9b and returns to the oil tank 9f, the control hydraulic pressure adjusting valve 52a and the sealing oil spill Regardless of the operating conditions, the hydraulic pressure discharged from the hydraulic pump 9a, that is, the minimum hydraulic pressure is generated in the control hydraulic line 52e by the resistance caused by passing through the valve 52b. And the oil pressure of the sealing oil pressure line 52d branched from the intermediate line 52c between the control oil pressure adjusting valve 52a and the sealing oil spill valve 52b is defined by the resistance of the sealing oil spill valve 52b regardless of the operating conditions.

Thus, the resistance provided in the sealing oil spill valve 52b is created by the resistance provided in the sealing oil spill valve 52b in the hydraulic oil discharged from the hydraulic pump 9a and returned to the oil tank 9f via the direction switching valve 9b. The hydraulic pressure of the sealing hydraulic line 52d is such that it becomes the minimum hydraulic pressure necessary for sealing the seal.
Further, the resistance provided in the control hydraulic pressure adjusting valve 52a is as follows. That is, the hydraulic pressure generated in the hydraulic oil line discharged from the hydraulic pump 9a, that is, the hydraulic pressure created in the control hydraulic pressure line 52e, is determined by the resistance of the resistance of the control hydraulic pressure adjusting valve 52a and the resistance of the sealing oil spill valve 52b. The hydraulic pressure is necessary to control the switching valve 9b.

Hereinafter, the operation and effect of the above-described configuration will be described.
As shown in FIG. 2, in the hydraulic oil line that is discharged from the hydraulic pump 9a and returns from the specified hydraulic line 9j to the oil tank 9f via the return oil line 9L, the control hydraulic pressure adjusting valve 52a and the sealing oil spill valve 52b The hydraulic fluid of the sealing hydraulic line 52d branched from the intermediate line 52c therebetween reaches the back of each seal from the sealing oil inlet 13a of the anti-shock valve block 10 through the sealing check valve 13b.

  Thus, since the space behind each seal is a closed space, there is no oil flow in the sealing hydraulic line 52d, and when the direction switching valve 9b is in the neutral position, the electromagnetic pilot valve 9c There is no oil flow in the control hydraulic line 52e. Accordingly, the total amount of oil discharged from the hydraulic pump 9a returns from the specified hydraulic line 9j to the return oil line 9L through the control hydraulic pressure adjusting valve 52a and the sealing oil spill valve 52b, and then to the oil tank 9f.

In this state, the hydraulic pressure in the sealing hydraulic line 52d becomes a hydraulic pressure defined by the resistance of the sealing oil spill valve 52b. This hydraulic pressure is provided in parallel with the sealing hydraulic pressure line 52d, even when the hydraulic fluid extracted from the hydraulic fluid chambers 5a to 5d as sealing hydraulic pressure is no longer present due to no load, or is activated. Even when the oil pressure in the oil chambers 5a to 5d becomes a negative pressure, it is a height at which a predetermined minimum necessary pressing force can be applied to the seal surface, and generally 1 to 2 kg / cm, although it depends on the seal conditions. ² . And the height of this hydraulic pressure will not be exceeded in any change in the operating state.

Further, the hydraulic pressure of the control hydraulic line 52e becomes a hydraulic pressure defined by the resistance of the control hydraulic pressure adjusting valve 52a and the sealing oil spill valve 52b. The hydraulic pressure is generally 5 to 10 kg / cm ^{2 although} it varies depending on the conditions of the control device.
Effect Even when the hydraulic oil extracted as the hydraulic pressure for sealing from the hydraulic oil chambers 5a to 5d provided in parallel with the sealing hydraulic pressure line 51d does not exist due to no load, or the hydraulic oil chamber Even when the hydraulic pressure becomes negative, a predetermined minimum necessary pressing force can be applied to the seal surface to maintain a stable sealing effect. In that case, the pressing force against the sealing surface does not exceed the minimum pressing force necessary. Thus, the friction and wear of the sealing surface is minimized. Furthermore, even when the sealing surface is worn, the effect is always constant, unlike the case of the corrugated spring 7.

  Further, the space behind the seal is not a closed space with a small volume as in the case of the conventional pressure valve 6. For this reason, the high pressure hydraulic oil does not always act on the back surface of the seal due to pressure accumulation, and the lubricating oil film on the sealing surface is not destroyed, and the friction and wear of the sealing surface are not promoted by the destruction of the lubricating oil film. .

Moreover, since the pressure valve 6 can be eliminated, it is possible to eliminate the possibility that it will drop into the machine.
Next, a third embodiment of the present invention will be described with reference to FIG. As shown in FIG. 3, the control oil pressure required to operate the direction switching valve 9b for switching the direction of the hydraulic oil applied to the hydraulic oil chambers 5a to 5d of the rotary vane type steering machine is coaxial with the hydraulic pump 9a. Is supplied through a control hydraulic line 9i and an electromagnetic pilot valve 9c from a control hydraulic pump 9g. A branch line 53a is branched from the control hydraulic line 9i, and a first control hydraulic pressure adjustment valve 53b and a second control hydraulic pressure adjustment valve 53c are provided in parallel on the branch line 53a. A first control hydraulic pressure adjusting valve 53b and a sealing oil spill valve 53d are provided in series. The outlet line of the sealing oil spill valve 53d is connected to the return oil line 9L to the tank. A sealing hydraulic line 53f is branched from an intermediate line 53e between the first control hydraulic pressure adjusting valve 53b and the sealing oil spill valve 53d, and the sealing hydraulic line 53f is connected to the sealing oil inlet 13a of the anti-shock valve block 10.

  The outlet line of the second control hydraulic pressure regulating valve 53c is connected to the return oil line 9L to the tank. A switching valve 53g is provided on the inlet side of the first control hydraulic pressure adjustment valve 53b and the second control hydraulic pressure adjustment valve 53c, and the first control hydraulic pressure adjustment valve 53b is controlled by the second control by detecting the loss of the hydraulic pressure in the sealing hydraulic line 53f. Switching to the hydraulic adjustment valve 53c is performed.

  The hydraulic pressure of the control hydraulic line 9i is such that the oil in the control hydraulic line 9i passes through the first control hydraulic adjustment valve 53b and the sealing oil spill valve 53d, or passes through the second control hydraulic adjustment valve 53c. It is defined by the resistance relief to the tank 9f. The hydraulic pressure of the sealing hydraulic line 53f is defined by the resistance with which the oil in the sealing hydraulic line 53f relieves to the oil tank 9f through the sealing oil spill valve 53d.

  Therefore, the resistance provided in the sealing oil spill valve 53d is a relief of the oil in the sealing hydraulic line 53f to the oil tank 9f so that the oil in the sealing hydraulic line 53f becomes the minimum hydraulic pressure for sealing the seal. It is the size that gives the quantity.

  Further, the resistance provided in the first control oil pressure adjusting valve 53b is controlled so that the oil in the control oil pressure line 9i becomes a necessary oil pressure for controlling the direction switching valve 9b together with the resistance of the sealing oil spill valve 53d. This is a size that gives the relief amount of the oil in the hydraulic line 9i to the oil tank 9f. Further, the resistance provided in the second control hydraulic pressure adjustment valve 53c is necessary for the oil in the control hydraulic pressure line 9i to control the direction switching valve 9b when the branch line 53a is switched to the second control hydraulic pressure adjustment valve 53c. This is a size that gives a relief amount of the oil in the control hydraulic line 9i to the oil tank 9f so as to obtain a proper hydraulic pressure.

  The discharge amount of the control hydraulic pump 9g includes the amount of oil necessary for operating the direction switching valve 9b and the amount of oil that always overflows from the first control hydraulic pressure adjustment valve 53b and the sealing oil spill valve 53d to the oil tank 9f. And the total amount.

Hereinafter, the operation and effect of the above-described configuration will be described.
Operation As shown in FIG. 3, the oil discharged from the control hydraulic pump 9g passes through the electromagnetic pilot valve 9c to the direction switching valve 9b, and from the intermediate line 53e of the branch line 53a to the sealing check valve 13b. It reaches the back of each seal.

  Thus, since the space behind each seal is a closed space, there is no oil flow in the sealing hydraulic line 53f, and when the direction switching valve 9b is in the neutral position, the electromagnetic pilot valve There is no oil flow in the control hydraulic line 9i leading to 9C. Accordingly, the total amount of oil discharged from the control hydraulic pump 9g overflows from the branch line 53a to the oil tank 9f through the first control hydraulic pressure adjustment valve 53b and the sealing oil spill valve 53d.

In this state, the hydraulic pressure in the sealing hydraulic line 53f becomes the hydraulic pressure defined by the resistance of the sealing oil spill valve 53d. This hydraulic pressure is provided in parallel with the sealing hydraulic pressure line 53f, even if the hydraulic oil extracted from the hydraulic oil chambers 5a to 5d as sealing hydraulic pressure is no longer present due to no load, Even when the oil pressure in the oil chambers 5a to 5d becomes a negative pressure, it is a height at which a certain minimum necessary pressing force can be applied to the seal surface, and generally 1 to 2 kg / cm, although it varies depending on the seal conditions. ² . And the height of this hydraulic pressure will not be exceeded in any change in the operating state.

Further, the hydraulic pressure of the control hydraulic pressure line 9i becomes a hydraulic pressure defined by the resistance of the first control hydraulic pressure adjusting valve 53b and the sealing oil spill valve 53d. Alternatively, when the branch line 53a is switched to the line of the second control hydraulic pressure adjustment valve 53c by the switching valve 53g, the hydraulic pressure is defined by the resistance of only the second control hydraulic pressure adjustment valve 53c. These oil pressures are generally 5 to 10 kg / cm ² , although they vary depending on the conditions of the control device.

In the above state, if the sealing oil led to the back surface of the seal loses hydraulic pressure due to damage of the seal in the event of a failure, the switching valve 53g detects the loss of the hydraulic pressure, and the branch line The line between the first control hydraulic pressure adjusting valve 53b and the sealing oil spill valve 53d of 53a is shut off and switched to the line of the second control hydraulic pressure adjusting valve 53c to secure the control hydraulic pressure. By sensing that the switching valve 53g has been switched, it is possible to detect from the outside that an abnormality has occurred in the seal.
Effect Even when the hydraulic oil extracted as the hydraulic pressure for sealing from the hydraulic oil chambers 5a to 5d provided in parallel with the sealing hydraulic pressure line 53f is no longer present due to no load, Even when the hydraulic pressure becomes negative, a predetermined minimum necessary pressing force can be applied to the seal surface to maintain a stable sealing effect. In that case, the pressing force against the sealing surface does not exceed the minimum pressing force necessary. Thus, the friction and wear of the sealing surface is minimized. Furthermore, even when the sealing surface is worn, the effect is always constant, unlike the case of the corrugated spring 7.

  Further, the space behind the seal is not a closed space with a small volume as in the case of the conventional pressure valve 6. For this reason, the high pressure hydraulic oil does not always act on the back surface of the seal due to pressure accumulation, and the lubricating oil film on the sealing surface is not destroyed, and the friction and wear of the sealing surface are not promoted by the destruction of the lubricating oil film. .

Moreover, since the pressure valve 6 can be eliminated, it is possible to eliminate the possibility that it will drop into the machine.
Furthermore, it is possible to detect from the outside that an abnormality such as breakage has occurred in the seal when the switching valve 53g is switched to the position of the second control hydraulic pressure adjustment valve 53c.

  Next, a fourth embodiment of the present invention will be described with reference to FIG. As shown in FIG. 4, a first control hydraulic pressure adjusting valve 54a and a sealing oil spill valve 54b are provided in series on a specified hydraulic line 9j from which hydraulic oil discharged from the hydraulic pump 9a exits the direction switching valve 9b, and sealing is performed. The outlet line of the oil spill valve 54b is connected to the return oil line 9L of the hydraulic oil to the oil tank 9f. The sealing hydraulic line 54d is branched from an intermediate line 54c between the first control hydraulic pressure adjusting valve 54a and the sealing oil spill valve 54b, and the sealing hydraulic line 54d is connected to the sealing oil inlet 13a of the anti-shock valve block 10. A second control hydraulic pressure adjusting valve 54f is provided in parallel with the first control hydraulic pressure adjusting valve 54a in the specified hydraulic line 9j from which the hydraulic oil exits the direction switching valve 9b, and an outlet line of the second control hydraulic pressure adjusting valve 54f is connected to the oil tank 9f. Connect i to the return oil line 9L. A switching valve 54g is provided on the inlet side of the first control hydraulic pressure adjustment valve 54a and the second control hydraulic pressure adjustment valve 54f, and the first control hydraulic pressure adjustment valve 54a is second controlled by detecting the loss of the hydraulic pressure in the sealing hydraulic line 54d. Switching to the hydraulic adjustment valve 54f is performed. The control hydraulic line 54e is branched from the discharge line of the hydraulic pump 9a, and this line 54e is guided to the direction switching valve 9b through the electromagnetic pilot valve 9c.

  As the discharge hydraulic pressure of the hydraulic pump 9a, the minimum hydraulic pressure is set by the following means, which becomes the control hydraulic pressure through the control hydraulic pressure line 54e. That is, in the line through which the hydraulic oil discharged from the hydraulic pump 9a passes through the return oil line 9L returned to the oil tank 9f through the specified hydraulic line 9f exiting the direction switching valve 9b, the first control hydraulic pressure adjusting valve 54a and Regardless of the operating conditions, the resistance caused by passing through the sealing oil spill valve 54b causes the hydraulic oil discharged from the hydraulic pump 9a, that is, the minimum hydraulic pressure to be generated in the control hydraulic line 54e. The hydraulic pressure of the sealing hydraulic line 54d branched from the intermediate line 54c between the first control hydraulic pressure adjusting valve 54a and the sealing oil spill valve 54b is defined by the resistance of the sealing oil spill valve 54b regardless of the operating conditions. The

  Thus, the resistance provided in the sealing oil spill valve 54b is created by the resistance provided in the sealing oil spill valve 54b in the hydraulic oil discharged from the hydraulic pump 9a and returned to the oil tank 9f via the direction switching valve 9b. The hydraulic pressure of the sealing hydraulic line 54d is such that it becomes the minimum hydraulic pressure necessary for sealing the seal.

  Further, the resistance provided in the first control hydraulic pressure adjusting valve 54a is as follows. That is, the hydraulic pressure created in the hydraulic oil line discharged from the hydraulic pump 9a, that is, the control hydraulic line 54e, is set by the resistance of the resistance of the first control hydraulic pressure adjusting valve 54a and the resistance of the sealing oil spill valve 54b. The hydraulic pressure is necessary to control the direction switching valve 9b.

  Further, the resistance provided in the second control hydraulic pressure adjustment valve 54f is equal to the resistance of the first control hydraulic pressure adjustment valve 54a and the resistance of the sealing oil spill valve 54b, and the second control hydraulic pressure adjustment valve 54f alone. Accordingly, the hydraulic pressure generated in the hydraulic oil line discharged from the hydraulic pump 9a, that is, the control hydraulic pressure line 54e, can be changed to a hydraulic pressure necessary for controlling the direction switching valve 9b.

Hereinafter, the operation and effect of the above-described configuration will be described.
As shown in FIG. 4, in the hydraulic oil line that is discharged from the hydraulic pump 9a and returns from the specified hydraulic line 9f to the oil tank 9f via the return oil line 9L, the first control hydraulic pressure adjusting valve 54a and the sealing oil spill valve 54b The hydraulic oil in the sealing hydraulic line 54d branched from the intermediate line 54c between the hydraulic oil reaches the back surface of each seal through the sealing oil inlet 13a of the anti-shock valve block 10 and the sealing check valve 13b.

  Thus, since the space behind each seal is a closed space, there is no oil flow in the sealing hydraulic line 54d, and when the direction switching valve 9b is in the neutral position, the electromagnetic pilot valve 9c There is no oil flow in the control hydraulic line 54e. Accordingly, the total amount of oil discharged from the hydraulic pump 9a passes through the first hydraulic pressure adjusting valve 54a and the sealing oil spill valve 54b from the specified hydraulic line 9j, returns to the return oil line 9L, and then returns to the oil tank 9f. .

In this state, the hydraulic pressure in the sealing hydraulic line 54d becomes a hydraulic pressure defined by the resistance of the sealing oil spill valve 54b. This hydraulic pressure is used even when the hydraulic oil extracted as the hydraulic pressure for sealing from the hydraulic oil chambers 5a to 5d provided in parallel with the sealing hydraulic line 54d does not exist due to no load, or the hydraulic oil Even when the hydraulic pressure in the chambers 5a to 5d becomes negative, it is a height at which a predetermined minimum necessary pressing force can be applied to the seal surface, and generally 1 to ² kg / cm ² , although it varies depending on the seal conditions. It is. And the height of this hydraulic pressure will not be exceeded in any change in the operating state.

Further, the hydraulic pressure of the control hydraulic line 9i becomes a hydraulic pressure defined by the resistance of the first control hydraulic pressure adjusting valve 54a and the sealing oil spill valve 54b. Alternatively, when the specified hydraulic pressure line 9j is switched to the line of the second control hydraulic pressure adjustment valve 54f by the switching valve 54g, the hydraulic pressure is determined by the resistance of only the second control hydraulic pressure adjustment valve 54f. These oil pressures are generally 5 to 10 kg / cm ² , although they vary depending on the conditions of the control device.

In the above state, when the sealing oil led to the back of the seal loses the hydraulic pressure due to the damage of the seal, etc., the switching valve 54g detects the loss of the hydraulic pressure, and the specified hydraulic pressure is detected. The line of the first control hydraulic pressure adjustment valve 54a and the sealing oil spill valve 54b in the line 9j is shut off and switched to the line of the second control hydraulic pressure adjustment valve 54f to ensure the control hydraulic pressure. By sensing that the switching valve 54g has been switched, it is possible to detect from the outside that an abnormality has occurred in the seal.
Effect Even when the hydraulic oil extracted as the hydraulic pressure for sealing from the hydraulic oil chambers 5a to 5d provided in parallel with the sealing hydraulic pressure line 54d does not exist due to no load, or the hydraulic pressure of the hydraulic oil chamber Even when the pressure becomes negative, a predetermined necessary minimum pressing force can be applied to the sealing surface to maintain a stable sealing effect. In that case, the pressing force against the sealing surface does not exceed the minimum pressing force necessary. Thus, the friction and wear of the sealing surface is minimized. Furthermore, even when the sealing surface is worn, the effect is always constant, unlike the case of the corrugated spring 7.

  Further, the space behind the seal is not a closed space with a small volume as in the case of the conventional pressure valve 6. For this reason, the high pressure hydraulic oil does not always act on the back surface of the seal due to pressure accumulation, and the lubricating oil film on the sealing surface is not destroyed, and the friction and wear of the sealing surface are not promoted by the destruction of the lubricating oil film. .

Further, since the pressure valve 6 can be eliminated, it is possible to eliminate the possibility that it will drop into the machine.
Furthermore, it is possible to detect from the outside that an abnormality such as breakage has occurred in the seal when the switching valve 54g is switched to the position of the second control hydraulic pressure adjusting valve 54f.

51a Branch line 51b Control oil pressure adjustment valve 51c Sealing oil spill valve 51d Intermediate line 51e Sealing oil pressure line 52a Control oil pressure adjustment valve 52b Sealing oil spill valve 52c Intermediate line 52d Sealing oil line 52e Control oil line 53a Branch line 53b First control oil pressure adjustment Valve 53c Second control hydraulic adjustment valve 53d Sealing oil spill valve 53e Intermediate line 53f Sealing hydraulic line 53g Switching valve 54a First control hydraulic adjustment valve 54b Sealing oil spill valve 54c Intermediate line 54d Sealing hydraulic line 54e Control hydraulic line 54f Second control Hydraulic adjustment valve 54g selector valve

Claims (4)

A rotor fitted and mounted on the rudder shaft, a housing that houses the rotor and forms a space for an oil chamber around the rotor, and an annular top cover that is disposed in an upper opening of the housing; A plurality of vanes are arranged at equally spaced positions along the circumferential direction, a plurality of segments are arranged at equally spaced positions along the circumferential direction of the inner peripheral surface of the housing, and the oil chamber space is formed by the vanes and the segments. The plurality of hydraulic oil chambers are divided into a plurality of hydraulic oil chambers. The plurality of hydraulic oil chambers are operated by a first group of hydraulic oil chambers that rotate the rotor in the left and right directions by the supplied pressure oil and a second group of operations that rotate in the left and right directions. It consists of two groups of oil chambers, and each of the vanes of the rotor has a radial front end surface and upper and lower end surfaces facing the back surface of the top cover and the inner peripheral surface and inner bottom surface of the housing, respectively. Form vertical and horizontal slits, insert vertical seals in sliding contact with the inner peripheral surface of the housing in the vertical slits, insert upper horizontal seals in sliding contact with the back surface of the top cover in the upper horizontal slits, and in the lower horizontal slits. Insert the lower horizontal seal that is in sliding contact with the inner bottom surface of the housing, and form each of the above seals from an elastic material. The back of the vertical seal communicates with the back of the upper and lower horizontal seals to apply contact pressure to the sliding surface. Pressure oil is applied to the back of the vertical seal, and one inflow / outflow hole communicating with the first group of hydraulic oil chambers, the other outflow / inflow hole communicating with the second group of hydraulic oil chambers, One anti-shock valve that flows pressure oil flowing in from one inflow / outflow hole to the other outflow / inflow hole, and the other anti-shock valve that flows pressure oil flowing in from the other outflow / inflow hole into one outflow / inflow hole The anti-vibration valve block with A Tariben type steering gear,
The top cover holds an annular upper ring seal in an upper ring slit formed in a portion facing the upper end surface of the rotor, and the housing is in a lower ring slit formed in a portion facing the lower end surface of the rotor. And the rotor has a balance hole communicating with the upper end surface radially inward of the upper ring seal and the lower end surface radially inward of the lower ring seal. An inlet of one check valve is connected to one branch oil passage branched from the outflow / inflow hole, and an inlet of the other check valve is connected to the other branch oil passage branched from the other outflow / inflow hole. A communication oil passage that communicates the outlet of the stop valve is provided in the anti-shock valve block, and an oil supply passage that connects the communication oil passage of the anti-shock valve block and the annular upper ring groove provided on the upper end surface of the rotor. A sealing oil hole is provided through the vane from the rotor. The sealing oil hole is provided between the shock valve block and the top cover, and communicates with the upper ring groove and the bottom surface of the vertical slit of the vane. The upper ring groove is formed on the upper ring seal. The hydraulic pump communicates with the inner peripheral side surface and the rear surface, communicates with the inner peripheral side surface and the rear surface of the lower ring seal through the balance hole, and discharges from the hydraulic pump to the hydraulic circuit that supplies the hydraulic oil to the hydraulic oil chamber. A directional control valve for switching the supply destination of the hydraulic fluid to one of the hydraulic oil chamber of the first group and the hydraulic oil chamber of the second group, and a control hydraulic pressure for controlling switching of the directional switching valve from a control hydraulic pressure line A control hydraulic pump for supplying to the electromagnetic pilot valve of the direction switching valve is provided, and the sealing valve block is provided with a sealing oil inlet, a sealing oil check valve, Rotary vane type provided with a sealing oil passage communicating with the oil inlet and the inlet side of the sealing oil check valve, and a sealing oil communication oil passage communicating with the outlet side of the sealing oil check valve and the communication oil passage In the steering machine,
A branch line is provided in the control hydraulic line from the discharge port of the control hydraulic pump to the electromagnetic pilot valve that controls the direction switching valve, and the control hydraulic pressure adjusting valve and the sealing oil spill valve are provided in series in the branch line. The outlet line was connected to the tank return oil line, the sealing hydraulic line was branched from the intermediate line between the control hydraulic pressure adjustment valve and the sealing oil spill valve, and the sealing hydraulic line was connected to the sealing oil inlet of the anti-shock valve block A sealing device for a rotary vane type steering machine.   A branch line is provided in the control hydraulic line from the discharge port of the control hydraulic pump to the electromagnetic pilot valve that controls the direction switching valve, and the first control hydraulic pressure adjustment valve and the second control hydraulic pressure adjustment valve are provided in parallel in the branch line; A first control hydraulic pressure adjusting valve and a sealing oil spill valve are provided in series, an outlet line of the sealing oil spill valve is connected to a tank return oil line, and an intermediate line between the first control hydraulic pressure adjusting valve and the sealing oil spill valve Branching off the sealing hydraulic line, connecting the outlet line of the second control hydraulic adjustment valve to the tank return oil line, and detecting the loss of the sealing hydraulic pressure to switch the first control hydraulic adjustment valve to the second control hydraulic adjustment valve 2. The rotary vane steering gear seat according to claim 1, wherein the switching valve is provided on an inlet side of the first control hydraulic pressure adjustment valve and the second control hydraulic pressure adjustment valve. Packaging equipment. A rotor fitted and mounted on the rudder shaft, a housing that houses the rotor and forms a space for an oil chamber around the rotor, and an annular top cover that is disposed in an upper opening of the housing; A plurality of vanes are arranged at equally spaced positions along the circumferential direction, a plurality of segments are arranged at equally spaced positions along the circumferential direction of the inner peripheral surface of the housing, and the oil chamber space is formed by the vanes and the segments. The plurality of hydraulic oil chambers are divided into a plurality of hydraulic oil chambers. The plurality of hydraulic oil chambers are operated by a first group of hydraulic oil chambers that rotate the rotor in the left and right directions by the supplied pressure oil and a second group of operations that rotate in the left and right directions. It consists of two groups of oil chambers, and each of the vanes of the rotor has a radial front end surface and upper and lower end surfaces facing the back surface of the top cover and the inner peripheral surface and inner bottom surface of the housing, respectively. Form vertical and horizontal slits, insert vertical seals in sliding contact with the inner peripheral surface of the housing in the vertical slits, insert upper horizontal seals in sliding contact with the back surface of the top cover in the upper horizontal slits, and in the lower horizontal slits. Insert the lower horizontal seal that is in sliding contact with the inner bottom surface of the housing, and form each of the above seals from an elastic material. The back of the vertical seal communicates with the back of the upper and lower horizontal seals to apply contact pressure to the sliding surface. Pressure oil is applied to the back of the vertical seal, and one inflow / outflow hole communicating with the first group of hydraulic oil chambers, the other outflow / inflow hole communicating with the second group of hydraulic oil chambers, One anti-shock valve that flows pressure oil flowing in from one inflow / outflow hole to the other outflow / inflow hole, and the other anti-shock valve that flows pressure oil flowing in from the other outflow / inflow hole into one outflow / inflow hole The anti-vibration valve block with A Tariben type steering gear,
The top cover holds an annular upper ring seal in an upper ring slit formed in a portion facing the upper end surface of the rotor, and the housing is in a lower ring slit formed in a portion facing the lower end surface of the rotor. And the rotor has a balance hole communicating with the upper end surface radially inward of the upper ring seal and the lower end surface radially inward of the lower ring seal. An inlet of one check valve is connected to one branch oil passage branched from the outflow / inflow hole, and an inlet of the other check valve is connected to the other branch oil passage branched from the other outflow / inflow hole. A communication oil passage that communicates the outlet of the stop valve is provided in the anti-shock valve block, and an oil supply passage that connects the communication oil passage of the anti-shock valve block and the annular upper ring groove provided on the upper end surface of the rotor. A sealing oil hole is provided through the vane from the rotor. The sealing oil hole is provided between the shock valve block and the top cover, and communicates with the upper ring groove and the bottom surface of the vertical slit of the vane. The upper ring groove is formed on the upper ring seal. The hydraulic pump communicates with the inner peripheral side surface and the rear surface, communicates with the inner peripheral side surface and the rear surface of the lower ring seal through the balance hole, and discharges from the hydraulic pump to the hydraulic circuit that supplies the hydraulic oil to the hydraulic oil chamber. There is provided a direction switching valve for switching the supply destination of the hydraulic oil to either the first group of hydraulic oil chambers or the second group of hydraulic oil chambers, and a return oil line from the direction switching valve to the oil tank. The control hydraulic pressure for controlling the switching of the direction switching valve is supplied from the discharge port side of the hydraulic pump to the electromagnetic pilot valve of the direction switching valve, and the pressure is applied to the return oil line. A valve is provided, and the above-described anti-shock valve block includes a sealing oil inlet, a sealing oil check valve, a sealing oil passage communicating with the sealing oil inlet and the inlet side of the sealing oil check valve, and a sealing oil reverse In the rotary vane type steering machine provided with the sealing oil communication oil passage communicating with the outlet side of the stop valve and the communication oil passage,
A control hydraulic pressure adjustment valve and a sealing oil spill valve are provided in series in the return oil line from the direction switching valve to the oil tank, and the sealing hydraulic line is branched from the return oil line between the control hydraulic pressure adjustment valve and the sealing oil spill valve. And a sealing device for a rotary vane type steering machine, wherein a sealing hydraulic line is connected to a sealing oil inlet of an anti-shock valve block.   A first control hydraulic pressure adjusting valve and a sealing oil spill valve are provided in series in a return oil line from the direction switching valve to the oil tank, and a sealing hydraulic pressure is supplied from the return oil line between the first control hydraulic pressure adjusting valve and the sealing oil spill valve. The line is branched, the sealing hydraulic line is connected to the sealing oil inlet of the anti-shock valve block, the second control hydraulic pressure adjusting valve is provided in parallel with the first control hydraulic pressure adjusting valve, and the outlet line of the second control hydraulic pressure adjusting valve Is connected to the tank return oil line, and the switching valve is configured to switch the first control hydraulic pressure adjustment valve to the second control hydraulic pressure adjustment valve by detecting the loss of the sealing hydraulic pressure. The sealing device for a rotary vane type steering machine according to claim 3, wherein the sealing device is provided on an inlet side with respect to the regulating valve.

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