JP4514617B2 - Seal structure in rotary vane type steering machine - Google Patents

Description

  The present invention relates to a seal structure in a rotary vane type steering machine which is one type of ship steering machine.

  A conventional rotary vane type steering machine has a housing 1 and a rotor 2 housed therein, for example, 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 at the edge of the distal end in the radial direction. Further, 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 at the edge of the tip 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 21 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 surface 21 of each, sealing action is performed.

  By the upper and lower ring seals 3b and 1f, the hydraulic oil in each of the hydraulic oil chambers 5a to 5d causes a minute gap between the upper end surface 2k of the rotor 2 and the top cover 3 and the lower end surface 21 of the rotor 2 and the housing 1. This prevents 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 a small gap between the inner bottom surface of the inner fluid bottom surface.

  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.

  30 shows the cross-sectional shapes of the horizontal seals 2f and 2h and the vertical seals 1d and 2j, and FIG. 31 shows the cross-sectional shapes of the ring seals 3b and 1f. As shown in FIGS. 30 and 31, 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 applying pressure oil guided from the hydraulic oil chambers 5a to 5d to the back surfaces 1m, 1n, 2s, 2t, 2u, and 3e, the respective sliding 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 hydraulic fluid guided from the hydraulic fluid chambers 5a to 5d to the seal back surfaces 1m, 1n, 2s, 2t, 2u, and 3e has its pressure inside the skirt portions 1o, 1p, 2v, 2w, 2x, and 3f. Faster than acting on the slits 1c, 1e, 2e, 2g, 2i, 3a and the gaps between the seals 1d, 1f, 2f, 2h, 2j, 3b and entering the skirts 1o, 1p, 2v, 2w, In order to prevent the action of 2x and 3f from being obstructed, when each skirt portion 1o, 1p, 2v, 2w, 2x, and 3f is inserted into each slit 1c, 1e, 2e, 2g, 2i, and 3a, By applying elastic deformation to the skirt portions 1o, 1p, 2v, 2w, 2x, 3f, the outer sides of the skirt portions 1o, 1p, 2v, 2w, 2x, 3f are slits 1c, 1e, 2e, 2g, 2i, 3a. On both sides The period has been pressing.

  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. 32 to 35 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 the high-pressure hydraulic fluid 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. Even if the pressure is low or zero, the space between the back surface 2u of the vertical seal 2j of the vane 2d and the vertical slit 2i and the segment 1b so that the seal surface pressure is applied to the seal surfaces 2r and 1k. In the space between the back surface 1m of the vertical seal 1d and the vertical slit 1c, corrugated leaf springs (not shown) having the following roles are interposed 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 spring is for applying a necessary minimum surface pressure to the seal surfaces 2r and 1k even if sufficient hydraulic pressure is not generated.

  In the conventional structure of the upper and lower ring seals 1f and 3b, as shown in FIG. 31, 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. 36, since the vane 2d is a rotating body, as shown in FIG. 36, 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. 36, the pressure valve 6 has a valve seat 6d screwed into both inlets 6b of the valve 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 an old structure, as shown in FIG. 37, pressure oil is applied from the hydraulic oil chamber (any one of 5a to 5d) on the high pressure side to the back surface 1m of the vertical seal 1d. Is leading. 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.

  However, if this is difficult due to the assembly structure of the segment 1b, for example, the oil passage is routed from the two hydraulic oil chambers 5a, 5b (or 5c, 5d) adjacent to each other across the segment 1b through the top cover 3, respectively. Take out and provide check valves on each of them, combine the outlets of both check valves into one oil passage, and make the oil passage into a hole drilled in the top cover 3 so as to communicate with the back 1m of the vertical seal 1d. Are connected (not shown).

  Next, as shown in FIG. 27, for the upper and lower ring seals 3b, 1f, an oil passage 3g leading from the upper end of the back surface 1m of the vertical seal 1d of the segment 1b to the back surface 3e of the upper ring seal 3b is a top cover 3 In addition, an oil passage 1q leading 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 drilled in the bottom portion of the housing 1, whereby a hydraulic oil chamber on the high pressure side is formed. Pressure oil from 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 the case of assembling a steering gear, the following methods have been conventionally used to mount the respective seals 1d, 1f, 2f, 2h, 2j, and 3b.
That is, as shown in FIG. 27, the lower ring seal 1f is inserted into the lower ring slit 1e at the inner bottom of the housing 1, and the lower horizontal seal 2h is inserted into the lower horizontal slit 2g of the vane 2d. The rotor 2 is assembled in the housing 1. In this assembled state, the vertical seal 2j of the vane 2d is press-fitted into the vertical slit 2i from above, and a corrugated spring (not shown) is press-fitted into the gap between the back surface 2u of the vertical seal 2j and the vertical slit 2i. To do. Thereafter, the upper horizontal seal 2f of the vane 2d is inserted into the upper horizontal slit 2e. Similarly, for the segment 1b, the vertical seal 1d is press-fitted into the vertical slit 1c from above, and a corrugated spring (not shown) is press-fitted into the gap between the back surface 1m of the vertical seal 1d and the vertical slit 1c. To do. Then, the upper ring seal 3 b is inserted into the upper ring slit 3 a of the top cover 3, and the top cover 3 is assembled to the housing 1.

  In order to supply hydraulic oil to the hydraulic oil chambers 5a to 5d of the rotary vane type steering machine assembled as described above, a hydraulic circuit as shown in FIG. 38 is provided. In FIG. 38, the circuit shown on the left side is a case where the control hydraulic pump 9g is provided, and the circuit shown on the right side is a case where the control hydraulic pump 9g is not provided. The hydraulic circuit includes, as main components, a hydraulic pump 9a having a one-way constant discharge amount, a direction switching valve 9b, an electromagnetic valve 9c for controlling the direction switching valve 9b, a pilot check valve 9d, and a flow rate adjusting valve 9e. And an oil tank 9f.

  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.

  Also, as shown on the left side of FIG. 38, is the control hydraulic pressure required for operating the direction switching valve 9b supplied from the control hydraulic pump 9g provided coaxially with the hydraulic pump 9a through the control hydraulic line 9i? Alternatively, as shown on the right side of FIG. 38, either method of using the discharge hydraulic pressure of the hydraulic pump 9a as the control hydraulic pressure of the direction switching valve 9b is taken. In the latter 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. The pressure adjusting valve 9h is provided on the return line 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 adjusting valve 9h is A specified hydraulic pressure line 9j is regulated to a constant pressure by the pressure regulating valve 9h.

  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. 38 and 39, the top cover 3 is provided with a hydraulic oil chamber. 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.
JP2003-161371

  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, once the pressure oil is introduced into the working hole 2z and the back surface 2u of the vertical seal 2j through the pressure valve 6, a sealed space is formed by the ball valve body 6e and the skirt portions 2x of the vertical seal 2j. Since the volume of this space is small, even after the hydraulic pressure of the hydraulic oil in each of the hydraulic oil chambers 5a to 5d decreases, the pressure oil accumulated in the space does not move the seal surface 2r of the vertical seal 2j from the back surface 2u. There was a problem that the pressure was kept pressing as much as necessary, thereby facilitating the wear of the seal surface 2r.

  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. As a result, the sealing surfaces 1g, 1k, 2p, 2q, 2r, and 3c are pressed against the mating surfaces to provide sealing properties. However, when the steering gear is unloaded or under low load, Since sufficient hydraulic pressure is not generated, the pressing force generated on each of the seal surfaces 1g, 1k, 2p, 2q, 2r, 3c is insufficient, and sufficient sealing performance cannot be obtained, and the hydraulic oil chambers 5a to 5d are not provided. There is a problem that hydraulic oil 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 corrugated springs (not shown) are respectively inserted in the spaces between 1 m and 2 u and the slits 1 c and 2 i and sufficient hydraulic pressure is not generated in the hydraulic oil chambers 5 a to 5 d, the corrugated springs described above are used. The initial surface pressure is applied to each of the seal surfaces 1k and 2r by the repulsive force. However, when the longitudinal seals 1d and 2j are inserted into the longitudinal slits 1c and 2i from above after the rotor 2 is mounted in the housing 1, the corrugated springs must be press-fitted together with the longitudinal seals 1d and 2j. Therefore, it is necessary to allow the corrugated spring to be press-fitted at a sacrifice of the spring force of the corrugated spring, and after the corrugated spring is inserted, the corrugated spring is worn by the seal surfaces 1k and 2r. There is a problem that the spring force of the leaf spring is reduced, so that a sufficient initial surface pressure cannot be applied to the sealing surfaces 1k and 2r.

  Further, the upper and lower side seals 2f and 2h of the vane 2d where the linear length of the sealing is short and no corrugated spring is provided, and the upper and lower portions where it is difficult to provide the corrugated spring on the back surface due to the ring shape. With respect to the ring seals 1f and 3b, there remains a problem that the sealing performance deteriorates when sufficient hydraulic pressure is not generated in the hydraulic oil chambers 5a to 5d.

  Furthermore, since the corrugated spring after being mounted is in a free state, it is difficult to keep the corrugated spring in an accurate position, and the position of the corrugated spring varies during operation of the steering gear, and each sealing surface 1k and 2r contact becomes uneven, resulting in variations in sealing performance and uneven wear of the seal surfaces 1k and 2r.

  The above problem is that during the operation of the rudder at a small rudder angle that occupies most of the ship's navigation, the steering frequency is reduced due to creeping effects due to the deterioration of the sealing performance of the steering. This means not only that the operation of the rudder will become unstable, but also that the wear of the rudder will be accelerated.

  Further, as shown in FIG. 30, for the vertical seal 2j of the vane 2d, the upper and lower horizontal seals 2f, 2h, and the vertical seal 1d of the segment 1b, high-pressure hydraulic oil is applied to the rear surfaces 2u, 2s, 2t, 1m. Each of the sealing surfaces 2r, 2p, 2q, and 1k is slid by pressing against the mating surfaces (the inner peripheral surface of the housing 1, the back surface of the top cover 3, the inner bottom surface of the housing 1, and the outer peripheral surface of the rotor 2). For example, when the rotor 2 rotates in one direction F, one end edge i of the seal surfaces 2r, 2p, 2q, and 1k acts as a scraper for oil, and then the other end edge B slides. Will move. Therefore, the other end edges B of the seal surfaces 2r, 2p, 2q, and 1k are slid in a state without lubrication, and there is a problem of promoting wear.

  Next, when assembling the steering gear, after installing the rotor 2 in the housing 1 for the vertical seal 2j of the vane 2d and the vertical seal 1d of the segment 1b, the vertical seals 1d and 2j are respectively inserted into the respective vertical slits. 1c and 2i are inserted from above. At this time, the skirt portions 1o and 2x need to be pushed in while being elastically deformed. However, since the lengths of the vertical seals 1d and 2j are long, the frictional force between the slits 1c and 2i is considerably large. Become a thing. For this reason, not only the insertion of the vertical seals 1d and 2j itself is a difficult task, but also the entire vertical seals 1d and 2j are forced to be deformed during the insertion into the slits 1c and 2i, and uniform insertion is performed. There was a problem that it was often impossible to wear. Such deformation of the vertical seals 1d and 2j not only deteriorates the sealing performance but also causes uneven wear of the vertical seals 1d and 2j.

  Further, for the vane 2d, the deformation of the vertical seal 2j as described above may cause a gap in the connecting portion between the vertical seal 2j and the upper and lower horizontal seals 2f and 2h, or prevent proper connection. There is a problem of increasing the leakage of hydraulic oil from the gap. In addition, there is a problem of causing irregular wear in the connecting portion, and after inserting the vertical seal 2j, the connection state between the lower end surface of the vertical seal 2j and the lower horizontal seal 2h is not visible at all, There was a problem that it was not possible to visually confirm whether or not the connection state was correct.

  Further, in order to check the state of each seal 1d, 2f, 2j, 2h or replace each seal 1d, 2f, 2j, 2h, the top side cover 2f of the vane 2d is simply removed from the top cover 3. However, the vertical seal 2j of the vane 2d and the vertical seal 1d of the segment 1b are slits 1c, 2i as an inversion of the above-mentioned difficulty when installed in the slits 1c, 2i. There is a problem that the vertical seals 2j and 1d may be damaged due to the difficulty in extracting them.

  Furthermore, as another method for avoiding this, after releasing the coupling between the rotor 2 and the rudder shaft, the rotor 2 is removed from the housing 1 to thereby remove the vertical seal 2j of the vane 2d and the vertical seal 1d of the segment 1b, respectively. There is a method of taking out from the slits 1c, 2i, but there is a problem that this is a very large work. Similarly, the lower horizontal seal 2h of the vane 2d has a problem that there is only a method for extracting the lower horizontal seal 2h after the rotor 2 is extracted from the housing 1, which is a very large work.

  Further, as described above in the background section based on FIGS. 32 to 35, the upper and lower horizontal seals 2f and 2h of the vane 2d and the vertical seal 2j are each subjected to a slight elastic compression in the longitudinal direction. When installed in the slits 2e, 2g, 2i, the elastic compression in the longitudinal direction of the horizontal seals 2f, 2h causes the skirt portions 2v, 2w of the horizontal seals 2f, 2h and the skirt portions 2x of the vertical seals 2j. It is extremely complicated to analyze the influence on the connection relationship with the skirt portion, and it is difficult to calculate in advance. For this reason, the skirt portions 2v and 2w of the upper and lower lateral seals 2f and 2h and the end surfaces of the notches are vertically Connecting the skirt portion 2x of the seal 2j with an appropriate contact surface pressure is coupled with a large allowable manufacturing error due to the fact that each of the seals 2f, 2h, 2j is an elastic material. There is a problem that Shii. When a gap is formed in the connecting part or the contact surface pressure at the connecting part becomes too small, there is a problem that the high-pressure hydraulic oil leaks to the low pressure side through the connecting part. On the contrary, if the contact surface pressure of the connecting part becomes too strong, not only is it difficult to mount the upper and lower horizontal seals 2f and 2h in the upper and lower horizontal slits 2e and 2g, but an excessive contact force is applied to the upper part. In addition, there is a problem that the contact surface pressure of the end surfaces of the lower horizontal seals 2f and 2h is affected, and the surface pressure of the upper and lower ends of the seal surface 2r of the vertical seal 2j is affected.

  As for the connecting portion between the vertical seal 2j and the lower horizontal seal 2h, since the lower horizontal seal 2h is already mounted in the lower horizontal slit 2g when the rotor 2 is assembled into the housing 1, the rotor 2 When the vertical seal 2j is inserted into the vertical slit 2i and inserted from above, the connecting portion between the vertical seal 2j and the lower horizontal seal 2h is in a state where it cannot be seen at all. Therefore, it is very difficult to make appropriate connection between the skirt portion 2x of the vertical seal 2j and the notch end surface of the skirt portion 2w of the lower horizontal seal 2h at the lower end portion of the vertical seal 2j. Even if the seals 1d, 2f, 2j, and 2h are compressed by mounting the top cover 3 with the lower end surface of the skirt portion 2x of the vertical seal 2j riding on the skirt portion 2w of the lower horizontal seal 2h. As described above, since visual inspection is not possible, the connecting portions of the vertical seal 2j and the upper and lower horizontal seals 2f and 2h may be abnormally elastically deformed with each other. In addition to increasing the leakage to the side, there was a problem of causing abnormal wear of the seal.

An object of this invention is to provide the seal structure in a rotary vane type steering machine as described in following (1)-(4).
(1) It is not necessary to provide a pressure valve on the vane that may drop off, and the means for guiding the pressure oil from the hydraulic oil chamber to the back of each seal is unified and simplified.
(2) By the above unification, even when no hydraulic pressure is generated in the hydraulic oil chamber, the hydraulic pressure of a predetermined value or more can be applied to the back surface of all the seals so that the sealing action can be performed reliably.
(3) By applying high pressure hydraulic oil to the back surface of the seal, even if a high contact surface pressure is applied to the seal surface, lubrication is ensured on the seal surface so that wear can be reduced.
(4) Eliminates problems at the joint between the vertical seal and the horizontal seal of the vane, and facilitates insertion / removal of the vertical seal of the vane, the lower horizontal seal, and the vertical seal of the segment, and causes abnormal deformation. Enables proper installation without any problems.

In order to solve the above-described problems, the first aspect of the present invention is arranged in a rotor fitted and mounted on a 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 equal intervals along the circumferential direction of the outer peripheral surface of the rotor, and a plurality of segments at equal intervals along the circumferential direction of the inner peripheral 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 are operated in a first group that rotates the rotor in one left-right direction by the supplied pressure oil. It consists of two groups of oil chambers and a second group of hydraulic oil chambers that rotate to the left and right in the other direction, and face each vane of the rotor to the back surface of the top cover and the inner peripheral surface and inner bottom surface of the housing, respectively. In addition, vertical and horizontal slits are formed at the front end edge in the radial direction and the upper and lower end faces, 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 upper horizontal slit is formed on the back surface of the top cover. Insert the upper horizontal seal that is in sliding contact, 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 seals with an elastic material, and the back of the vertical seal is the back of the upper and lower horizontal seals Pressure oil is applied to the back of the vertical seal so that the contact surface pressure is applied to the sliding surface.
One inflow / outflow hole communicating with the hydraulic oil chamber of the first group, the other outflow / inflow hole communicating with the hydraulic oil chamber of the second group, and the pressure oil flowing in from the one outflow / inflow hole into the other outflow / inflow hole Rotary vane rudder in which an anti-vibration valve block having one anti-vibration valve flowing out to the other and another anti-vibration valve flowing pressure oil flowing in from the other outflow / inflow hole to the one outflow / inflow hole is arranged A seal structure in a take-up machine,
An inlet of one check valve is connected to one branch oil passage branched from the one 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 communicating with the outlets of both check valves is provided in the anti-shock valve block, and the oil supply is made to communicate the communication oil passage of the anti-shock valve block with the annular upper ring groove provided on the upper end surface of the rotor. A passage is provided between the impact valve block and the top cover, and a sealing oil hole that communicates the upper ring groove and the bottom surface of the vertical slit of the vane is provided from the rotor through the vane.

  According to this, when an abnormally large impact load acts on the rudder and, for example, the hydraulic pressure of the hydraulic oil chamber of the first group rises abnormally, the hydraulic oil of the hydraulic oil chamber of the first group is discharged from one outflow / inlet hole. Inflow, one of the shock-proof valves is activated, and the pressure oil flows out into the other outflow / inlet hole. As a result, the pressure oil is discharged from the other inflow / outflow hole and escapes to the hydraulic oil chamber of the second group, so that the impact load is reduced. Similarly, when the hydraulic pressure of the hydraulic oil chamber of the second group rises abnormally, the pressure oil in the hydraulic oil chamber of the second group escapes to the hydraulic oil chamber of the first group, so that the impact load is alleviated.

  The inlet of one check valve is always in communication with the hydraulic oil chamber of the first group through one branch oil passage, and the inlet of the other check valve is in the second group through the other branch oil passage. It is always in communication with the hydraulic oil chamber. For example, when the hydraulic pressure of the hydraulic oil chamber of the first group is higher than the hydraulic pressure of the hydraulic oil chamber of the second group, the hydraulic oil in the hydraulic oil chamber of the first group opens one check valve and opens the communication oil passage. And the other check valve is prevented from flowing into the hydraulic oil chamber of the second group, which is on the low pressure side, and is supplied from the communication oil passage through the oil supply passage to the upper ring groove and from the upper ring groove to the sealing oil. It is introduced to the bottom of the vertical slit through the hole, and further, the back of the vertical seal is connected to the back of the upper and lower horizontal seals, so it is also introduced from the back of the vertical seal to the back of the upper and lower horizontal seals. Is done. Accordingly, high pressure oil acts on the back surface of the vertical seal and the back surfaces of the upper and lower horizontal seals, and a reliable sealing action is exhibited by the vertical seal and the upper and lower horizontal seals. On the contrary, when the hydraulic pressure of the hydraulic oil chamber of the second group is higher than the hydraulic pressure of the hydraulic oil chamber of the first group, similarly, the hydraulic oil of the hydraulic oil chamber of the second group is the bottom surface of the vertical slit. To be introduced.

  In addition, all of the pressure oil required to cause the vertical seal and the upper and lower horizontal seals to seal is supplied from the hydraulic oil chamber on the high-pressure side via the anti-shock valve block. Therefore, there is no need to provide the vane with a pressure valve that has a possibility of dropping as in the conventional case, the problem of dropping off the pressure valve is solved, and the means for guiding the pressure oil can be unified and simplified. .

  The second aspect of the present invention is directed to a hydraulic circuit that supplies hydraulic oil to the hydraulic oil chamber, a direction switching valve that switches a hydraulic oil supply destination to either the first group of hydraulic oil chambers or the second group of hydraulic oil chambers; There is provided a control hydraulic pump for supplying a control hydraulic pressure for controlling the switching of the direction switching valve from the control hydraulic line to the direction switching valve, a pilot oil inflow port, a pilot oil check valve, a pilot A pilot oil passage communicating with the oil inlet and the inlet side of the pilot oil check valve and a pilot oil communication oil passage communicating with the outlet side of the pilot oil check valve and the communication oil passage are provided. The pilot oil inlet of the valve block communicates with the control hydraulic line.

  According to this, when the hydraulic pressure required for the sealing action is not generated in the hydraulic oil chambers of the first and second groups, and this hydraulic pressure is lower than the hydraulic pressure of the control hydraulic line, the control hydraulic line The hydraulic pressure supplied to the pilot oil passage from the pilot oil inlet opens the pilot oil check valve, is supplied to the communication oil passage through the pilot oil communication oil passage, and passes through the oil supply passage from the communication oil passage. It is supplied to the upper ring groove, introduced from the upper ring groove through the sealing oil hole to the bottom surface of the vertical slit, and further introduced from the back side of the vertical seal to the back side of the upper and lower horizontal seals. The upper and lower side seals are sealed, and one and the other check valves are given a check action to prevent the hydraulic pressure from leaking to the hydraulic oil chambers.

  If the hydraulic pressure generated in each hydraulic oil chamber is higher than the hydraulic pressure in the control hydraulic line, the hydraulic pressure in the hydraulic oil chamber is introduced to the bottom surface of the vertical slit in the same manner as in the first invention, and the vertical seal and the upper and lower portions are A sealing action is applied to the horizontal seal.

  Therefore, even when the steering gear is unloaded or lightly loaded and the hydraulic pressure necessary for sealing is not generated in the hydraulic oil chamber, the hydraulic pressure of the control hydraulic line is at least the upper and lower parts of the vane vertical seal. Since it acts on the lower side seal and the lower side seal, the sealing action is always performed with a hydraulic pressure exceeding a certain minimum value, and a reliable sealing action is performed in any state. . Therefore, the steering performance of the steering gear is ensured even during the operation of the rudder at a small rudder angle that occupies most of the ship's sailing, that is, even when the steering gear is operating at low or no load. Therefore, creeping of the steering gear due to a decrease in sealing performance is prevented, and an increase in the operating frequency of the steering gear can be avoided. Therefore, not only is the operation of the rudder stabilized, but also the wear of the rudder is reduced.

  Furthermore, unlike the conventional case, it is no longer necessary to press-fit a corrugated spring on the back of the vertical seal, so that the conventional problems associated with the use of corrugated springs are eliminated, and the deterioration and deterioration of the sealing function can be avoided. Can be made uniform, and uneven wear of the seal surface of the vertical seal can be prevented.

  According to the third aspect of the present invention, the supply destination of the hydraulic oil discharged from the hydraulic pump is set to any one of the first group of hydraulic oil chambers and the second group of hydraulic oil chambers. And a return oil line from the direction switching valve to the oil tank, a pressure adjusting valve is provided in the return oil line, and the control hydraulic pressure for controlling the switching of the direction switching valve is controlled by the hydraulic pump. The discharge valve side is configured to supply to the direction switching valve, and the line between the direction switching valve and the pressure regulating valve is formed as a specified hydraulic pressure line that is defined as a certain hydraulic pressure or more, A pilot oil inlet, a pilot oil check valve, a pilot oil passage communicating with the pilot oil inlet and the inlet side of the pilot oil check valve, and an outlet side and a communicating oil passage of the pilot oil check valve. Communicating pilot A communicating oil passage is provided, in which the pilot oil inlet of the explosion 衝弁 block communicates with the discharge side of the prescribed hydraulic line or hydraulic pump line.

  According to this, sufficient hydraulic pressure necessary for the sealing action is not generated in the hydraulic oil chambers of the first and second groups, and this hydraulic pressure is not supplied to the specified hydraulic line (or the discharge side line of the hydraulic pump). When it is lower than the hydraulic pressure, the hydraulic pressure supplied from the specified hydraulic line (or the discharge side of the hydraulic pump) through the pilot oil inlet to the pilot oil passage pushes the pilot oil check valve open, and the pilot oil communication The oil is supplied to the communication oil passage through the oil passage, supplied to the upper ring groove from the communication oil passage through the oil supply passage, introduced from the upper ring groove to the bottom surface of the vertical slit through the sealing oil hole, and It is also introduced from the back side to the back side of the upper and lower horizontal seals, and causes the vertical seal of the vane and the upper and lower horizontal seals to seal, and one and the other check valve Giving non-return effect, you prevent the hydraulic pressure from leaking to the hydraulic oil chamber.

  Further, if the hydraulic pressure generated in each hydraulic oil chamber becomes higher than the hydraulic pressure of the specified hydraulic line, the hydraulic oil pressure in the hydraulic oil chamber is introduced to the bottom surface of the vertical slit in the same manner as in the first invention, and the vertical seal and the upper and lower portions are A sealing action is applied to the horizontal seal.

  Therefore, even when the steering gear is unloaded or lightly loaded and the hydraulic pressure necessary for sealing is not generated in the hydraulic oil chamber, at least the prescribed hydraulic line (or the hydraulic pump discharge side line) ) Will act on the vertical seal of the vane and the upper and lower horizontal seals. Therefore, the sealing action will always be performed by the hydraulic pressure exceeding the minimum required constant value. A reliable sealing action will be performed.

  This prevents creeping due to reduced sealing performance during the rudder operation at a small rudder angle, which occupies most of the ship's navigation, and avoids an increase in the frequency of operation of the steering gear. Not only is the operation of the rudder stabilized, but also the wear of the rudder is reduced.

The fourth invention includes a rotor fitted to and mounted on the rudder shaft, a housing that houses the rotor and forms a space for the oil chamber around the rotor, and an annular top cover that is disposed in the upper opening of the housing. A plurality of vanes are arranged at equally spaced positions along the circumferential direction of the outer peripheral surface of the rotor, and a plurality of segments are arranged at equally spaced positions along the circumferential direction of the inner circumferential surface of the housing. A seal structure in a rotary vane type steering machine that divides the oil chamber space into a plurality of hydraulic oil chambers,
A curved portion that is curved in an arc shape is formed in the lower corner portion of the tip surface of the vane, and an arc-shaped bent portion that is opposed to the curved portion of the vane is formed in the lower corner portion of the inner peripheral surface of the housing, An upper horizontal slit is formed in the upper end surface of the vane, and an upper horizontal seal that is slidably contacted with the back surface of the top cover is inserted into the upper horizontal slit. The radial direction of the lower end of the rotor passes through the bent portion from the tip surface of the vane. A curved slit that reaches the end surface is formed in the vane, and a curved seal that is in sliding contact with the inner peripheral surface and the inner bottom surface of the housing is inserted into the curved slit, and each of the seals is formed of an elastic material,
The curved seal protrudes from the both sides of the back surface formed on the opposite side of the base, the sealing surface that is in sliding contact with the inner peripheral surface and the inner bottom surface of the housing, and toward the back side of the curved slit. A pair of skirt portions opposed to each other in the direction, and the distal end portion of the skirt portion slightly protrudes outward in the circumferential direction from the side surface of the base portion in a free state before mounting.
The curved slit is composed of a bottom surface and a pair of side surfaces facing each other in the circumferential direction of the rotor, and the vane is divided into a vane body and a seal restrainer that can be attached to and detached from the vane body. The bottom surface and one side surface of the slit are formed, the other side surface of the curved slit is formed to suppress the seal, and the other side of the curved slit is opened in a state where the seal suppressor is removed from the vane body.

  According to this, since the conventional vertical seal and the lower horizontal seal are not connected, the above-described conventional problems associated therewith are solved. Furthermore, when assembling the rotor to the housing, the rotor is housed in the housing with the seal restrainer removed from the vane body. With the seal restrainer removed from the vane body, the other side of the curved slit is open, and the bottom and one side of the curved slit are exposed in the space of the hydraulic oil chamber. Using the space, the bent seal is inserted into the bent slit of the vane body from the other side where the bent slit is opened, and then the seal restrainer is attached to the vane body. At this time, the skirt portion of the bent seal is elastically compressed to a normal insertion state. Thereafter, the upper horizontal seal is inserted into the upper horizontal slit from above.

  Accordingly, the bent seal can be easily and accurately attached to the vane while visually confirming. Also, the vane seal can be inspected for openness without lifting the rotor off the rudder shaft.

In the fifth aspect of the present invention, an oil groove is formed in the longitudinal direction in the center of the seal surface in the circumferential direction, and a space between the bottom of the oil groove and the skirt on the back side or the bottom and back of the oil groove. A fine oil hole communicating with the side recess is formed at the base of the seal.

According to this, a small amount of hydraulic oil is supplied to the oil groove through the fine oil hole out of the hydraulic oil introduced from the hydraulic oil chamber into the space between the two skirts on the back side of the seal or the concave on the back side. The
For example, when the seal is a vertical seal, when the rotor rotates in one left-right direction and the seal surface of the vertical seal slides in one direction with respect to the inner peripheral surface of the housing, the edge on one side of the seal surface Acts as a scraper on the oil and breaks the lubrication by the hydraulic oil between the seal surface and the inner peripheral surface of the housing, but the oil groove is filled with the hydraulic oil. It is avoided that the portion on the other side of the oil groove slides without lubrication, and lubrication of the portion on the other side of the oil groove on the seal surface is ensured. Therefore, it is possible to prevent the sliding in the state without lubrication due to the scraper action and the promotion of the wear due to the scraper action, which has been a problem in the past. Similar effects can be obtained when the seal is a curved seal, an upper horizontal seal, or a lower horizontal seal.

A first embodiment of the present invention will be described below with reference to FIGS.
Note that members that perform basically the same operations as those of the conventional members described above with reference to FIGS. 27 to 39 are denoted by the same reference numerals and description thereof is omitted.

  The plurality of hydraulic oil chambers 5a to 5d are arranged at the counter electrode to rotate the rotor 2 in the left and right direction, and the first group of hydraulic oil chambers 5a and 5c and are arranged at the counter electrode to rotate the rotor 2 in the left and right directions. It consists of two groups of hydraulic oil chambers 5b and 5d of the second group. In addition, at the upper and lower ends of the vertical seal 2j of the vane 2d, the back surface 2u of the vertical seal 2j communicates with the back surfaces 2s and 2t of the upper and lower horizontal seals 2f and 2h, respectively.

First, means for guiding pressure oil to the back surfaces 2s, 2t, and 2u with respect to the seals 2f, 2h, and 2j of the vane 2d of the rotor 2 that is a rotating body will be described.
As shown in FIG. 1, an anti-impact valve block 10 is provided on the upper surface of the top cover 3. As shown in FIGS. 4 to 6, the anti-impact valve block 10 has one inflow / outflow hole 10a and the other inflow / outflow. Hole 10b is formed, one outflow / inflow hole 10a communicates with one oil passage 3h formed in the top cover 3, and the other outflow / inflow hole 10b is the other oil passage formed in the top cover 3. It communicates with 3i. 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 these anti-shock valves 8c and 8d have the same configuration as the conventional one shown in FIG.
The one outflow / inflow hole 10a communicates with the inflow side of one of the anti-shock valves 8c and the outflow side of the other anti-shock valve 8d, and the other outflow / inflow hole 10b communicates with the inflow side of the other anti-shock valve 8d and It communicates with the outflow side of the impulse valve 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. 1 and 2, an annular upper ring groove 11a is provided in the upper end surface 2k of the rotor 2, and the upper ring groove 11a and the pressure oil extraction port 10k of the anti-shock valve block 10 are communicated 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.

  1 and 3, 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, The lower ring slit 1e provided on the inner bottom surface of the housing 1 also communicates with the inner peripheral edge.

  Further, as shown in FIG. 1, a sealing oil hole 11b is formed in 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 lower end opening communicates with the bottom surface of the vertical slit 2i of the vane 2d (see FIG. 13).

Hereinafter, the operation of the above-described configuration will be described.
As shown in FIGS. 4 to 6, one check valve 10g of the anti-shock valve block 10 is connected to the first group of hydraulic oil chambers 5a and 5c via one branch oil passage 10c and a rising oil passage 10e. The other check valve 10h is always in communication with both hydraulic oil chambers 5b and 5d of the second group through the other branch oil passage 10d and the rising oil passage 10f.

  For this reason, among the hydraulic oil chambers 5a, 5c of the first group and the hydraulic oil chambers 5b, 5d of the second group, the hydraulic oil chamber of the higher hydraulic pressure group, for example, the hydraulic oil chambers 5a, 5c. Is blocked from flowing into the hydraulic oil chambers 5b and 5d on the low pressure side by opening the one check valve 10g and leading to the communication oil passage 10i, and the other check valve 10h. 10j to the pressure oil extraction port 10k, and through the pressure oil extraction port 10k of the anti-shock valve block 10 through the cover side oil supply passage 12a as shown in FIGS. 1 and 2, the upper ring of the rotor 2 It is supplied to the groove 11a, is introduced from the upper ring groove 11a through the sealing oil hole 11b (see FIGS. 1 and 13) to the bottom surface of the vertical slit 2i of each vane 2d, and acts on the back surface 2u of the vertical seal 2j.

  Further, since the back surface 2u of the vertical seal 2j communicates with the back surfaces 2s and 2t of the upper and lower horizontal seals 2f and 2h, the pressure oil introduced into the vertical seal back surface 2u is transferred to the upper and lower horizontal seals 2f and 2t. It is also introduced and acts on the rear surfaces 2s and 2t of 2h, and causes the sealing surfaces 2r, 2p and 2q of the vertical seal 2j and the upper and lower horizontal seals 2f and 2h to perform a sealing action. Thus, a reliable sealing action is exhibited by the vertical seal 2j and the upper and lower horizontal seals 2f and 2h.

  On the contrary, when the hydraulic pressures of the hydraulic oil chambers 5b and 5d of the second group are higher than the hydraulic pressures of the hydraulic oil chambers 5a and 5c of the first group, the hydraulic oils of the second group are similarly changed. The hydraulic pressure in the chambers 5b and 5d is introduced into the bottom surface of the vertical slit 2i of each vane 2d.

  Further, as shown in FIG. 2, since the upper ring groove 11a communicates with the inner peripheral edge of the upper ring slit 3a, for example, in JP 2003-161371 “sealing structure of a rotary vane type steering machine” In the case of the ring seal structure shown in claim 3 and claim 4, the pressure oil in the upper ring groove 11a acts on the inner peripheral side surface of the upper ring seal 3b to push the upper ring seal 3b in the outer peripheral direction. Thus, it is possible to reliably prevent the hydraulic oil in the high-pressure hydraulic oil chamber (5a, 5c or 5b, 5d) from leaking from the outer peripheral side surface of the upper ring seal 3b. At the same time, the pressure oil also acts on the back surface 3e of the upper ring seal 3b and presses the seal surface 3c against the upper end surface 2k of the rotor 2, so that the inside of the high pressure hydraulic oil chamber (5a, 5c or 5b, 5d) It is possible to reliably prevent the hydraulic oil from leaking from the seal surface 3c of the upper ring seal 3b.

  Further, as shown in FIG. 3, the pressure oil is supplied from the upper ring groove 11a of the rotor 2 to the lower ring groove 11c through the balance hole 2m and from the lower ring groove 11c to the inner peripheral side end of the lower ring slit 1e. In order to communicate with the edge portion, the hydraulic oil in the high-pressure hydraulic oil chamber (5a, 5c or 5b, 5d) leaks from the outer peripheral side surface of the lower ring seal 1f and the seal surface 1g in the same manner as the upper ring seal 3b. Can be surely prevented.

  When the vertical seal 1d of the segment 1b has the structure shown in claims 6 and 7 of JP-A No. 2003-161371 “Sealing structure of a rotary vane type steering machine”, a high pressure is applied to the back surface of the vertical seal 1d. However, in the case of the vertical seal 1d of the segment 1b having the same configuration as that of the conventional one, as shown by the phantom line in FIG. The oil hole 3j is drilled so that the bottom surface of the upper ring slit 3a communicates with the upper end of the vertical seal 1d of each segment 1b.

  As a result, the pressure oil extracted from the hydraulic oil chamber (5a, 5c or 5b, 5d) on the high pressure side through the anti-shock valve block 10 also acts on the back surface 1m of the vertical seal 1d of the segment 1b. A sealing action is applied to the seal surface 1k of the vertical seal 1d.

  As described above, all of the pressure oil required to perform the sealing action of the respective seals 1d, 1f, 2f, 2h, 2j, and 3b is on the high pressure side through the anti-shock valve block 10. It will be extracted and supplied from the hydraulic oil chamber (5a, 5c or 5b, 5d), and therefore traverses the conventional vane 2d shown in FIGS. 36 and 37 (possibly also in the segment 1b). The pressure valve 6 that had to be provided can be eliminated, and the problem of dropping off of the pressure valve 6 can be solved. Further, since the means for guiding the pressure oil required for performing the sealing action is unified, it is simplified.

Next, a second embodiment of the present invention will be described with reference to FIGS.
7 to 9 show an anti-impact valve block 13 that is a means for guiding pressure oil to the back of the seals 2f, 2h, 2j of the vane 2d of the rotor 2. FIG.

  In the above-described anti-vibration valve block 13, the same inflow / outflow holes 10a, 10b, the anti-vibration valves 8c, 8d, the branch oil passages 10c, 10d, the rising oil passages 10e, 10f, and the like in the first embodiment, Check valves 10g and 10h, a communication oil passage 10i, a block-side oil supply passage 10j, and a pressure oil extraction port 10k are provided, and in addition to this, a pilot oil introduction means is provided.

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

  As shown in the left side circuit of FIG. 10, in the hydraulic circuit for supplying the hydraulic oil to the hydraulic oil chambers 5a to 5d, the supply destination of the hydraulic oil discharged from the hydraulic pump 9a is set to the first group of hydraulic oil chambers 5a, A control valve 9b for switching to one of the hydraulic oil chambers 5b and 5d of the second group and a control hydraulic pressure for controlling switching of the direction switching valve 9b is supplied from the control hydraulic pressure line 9i to the direction switching valve 9b. A hydraulic pump 9g is provided. The pilot oil inlet 13a communicates with the control hydraulic line 9i that extends from the control hydraulic pump 9g to the direction switching valve 9b.

Hereinafter, the operation of the above-described configuration will be described.
As shown in the left side circuits of FIGS. 7 to 9 and FIG. 10, the check valves 10g and 10h of the anti-shock valve block 13 are each of the first group as described in the first embodiment. The hydraulic oil chambers 5a and 5c and the second group of hydraulic oil chambers 5b and 5d are always in communication. The pilot oil check valve 13b is always in communication with the control hydraulic line 9i as shown in the left side circuit of FIG.

  For example, when the hydraulic pressure of the hydraulic oil chambers 5a and 5c of the first group is higher than the hydraulic pressure of the hydraulic oil chambers 5b and 5d of the second group and higher than the hydraulic pressure of the control hydraulic pressure line 9i, the hydraulic oil chamber 5a , 5c pushes and opens one check valve 10g and applies a check action to the other check valve 10h to prevent the oil pressure from leaking to the low-pressure side hydraulic oil chambers 5b and 5d. Further, a check action is applied to the pilot oil check valve 13b from the other end of the communication oil path 10i through the pilot oil communication oil path 13d to prevent the hydraulic pressure from leaking to the control hydraulic line 9i.

  Then, the pressure oil that has exited one check valve 10g acts on the back surface 2u of the vertical seal 2j of the vane 2d, and the upper and lower horizontal seals 2f, It also acts on the rear surfaces 2s and 2t of 2h to cause the sealing surfaces 2r, 2p and 2q of the vertical seal 2j and the upper and lower horizontal seals 2f and 2h to perform a sealing action. Further, the hydraulic pressure communicates with the upper and lower ring seals 3b and 1f to cause the upper and lower ring seals 3b and 1f to perform a sealing action.

  On the other hand, when the hydraulic pressure of the hydraulic oil chambers 5b, 5d of the second group is higher than the hydraulic pressure of the hydraulic oil chambers 5a, 5c of the first group and higher than the hydraulic pressure of the control hydraulic pressure line 9i, The hydraulic pressure of the hydraulic oil chambers 5b and 5d of the group pushes and opens the other check valve 10h to communicate with the respective seals 2j, 2f, 2h, 3b, and 1f and perform a sealing action, respectively. A check action is applied to the valve 10g and the pilot oil check valve 13b to prevent the hydraulic pressure from leaking to the low-pressure side hydraulic oil chambers 5a and 5c and to the control hydraulic pressure line 9i.

  When the hydraulic oil chambers 5a, 5b, 5c, and 5d do not have sufficient hydraulic pressure necessary for the sealing action and this hydraulic pressure is lower than the hydraulic pressure of the control hydraulic line 9i, the control hydraulic line 9i From the pilot oil inlet 13a to the pilot oil passage 13c pushes the pilot oil check valve 13b open and is supplied to the communication oil passage 10i through the pilot oil communication oil passage 13d. As in the first embodiment, the block-side and cover-side oil supply passages 10j, 12a communicate with the respective seals 2j, 2f, 2h, 3b, 1f to perform the sealing action, and the check valves 10g, 10h are non-returned. By acting, this hydraulic pressure is prevented from leaking to each hydraulic oil chamber 5a, 5b, 5c, 5d.

Further, by making the oil hole 3j shown by the phantom line in FIG. 2 of the first embodiment, the vertical seal 1d can be sealed.
Therefore, even when the steering gear is unloaded or lightly loaded and the hydraulic pressure necessary for sealing is not generated in the hydraulic oil chambers 5a, 5b, 5c, 5d, at least the control hydraulic line 9i Since the hydraulic pressure acts on each of the seals 2j, 2f, 2h, 3b, 1f, 1d, the sealing action is always performed with the hydraulic pressure exceeding the minimum required constant value, and in any state A reliable sealing action will be performed. Therefore, the steering performance of the steering gear is ensured even during the operation of the rudder at a small rudder angle that occupies most of the ship's sailing, that is, even when the steering gear is operating at low or no load. Therefore, creeping of the steering gear due to a decrease in sealing performance is prevented, and an increase in the operating frequency of the steering gear can be avoided. Therefore, not only is the operation of the rudder stabilized, but also the wear of the rudder is reduced.

  Further, unlike the prior art, it is no longer necessary to press the corrugated springs into the back surface 2u of the vertical seal 2j of the vane 2d and the back surface 1m of the vertical seal 1d of the segment 1b, thereby eliminating the conventional problems associated with the use of corrugated springs. In addition, it is possible to make the sealing performance uniform and prevent uneven wear of the seal surfaces 1k and 2r.

  In the second embodiment, the control hydraulic pump 9g is provided in the hydraulic circuit as shown in the left circuit of FIG. 10, but in the third embodiment described below, as shown in the right circuit of FIG. Furthermore, the control hydraulic pump 9g is not provided in the hydraulic circuit. That is, the hydraulic circuit is provided with a direction switching valve 9b and a return oil line through which hydraulic oil discharged from the hydraulic pump 9a is returned to the oil tank 9f via the direction switching valve 9b. The return oil line is provided with a pressure regulating valve 9h, and a hydraulic circuit is configured so that a control hydraulic pressure for controlling the switching of the direction switching valve 9b is supplied from the discharge port side of the hydraulic pump 9a to the direction switching valve 9b. Yes. A line between the direction switching valve 9b and the pressure regulating valve 9h is formed as a specified hydraulic pressure line 9j that is specified to be equal to or higher than a certain hydraulic pressure. The pilot oil inlet 13a communicates with a specified hydraulic line 9j.

Hereinafter, the operation of the above configuration will be described.
The pilot oil check valve 13b is always in communication with the specified hydraulic line 9j as shown in the right side circuit of FIG.

  For example, when the hydraulic pressure of the hydraulic oil chambers 5a, 5c of the first group is higher than the hydraulic pressure of the hydraulic oil chambers 5b, 5d of the second group and higher than the hydraulic pressure of the specified hydraulic line 9j, the hydraulic oil chamber 5a , 5c pushes and opens one check valve 10g and applies a check action to the other check valve 10h to prevent the oil pressure from leaking to the low-pressure side hydraulic oil chambers 5b and 5d. Further, a check action is applied to the pilot oil check valve 13b from the other end of the communication oil path 10i through the pilot oil communication oil path 13d, and this hydraulic pressure is prevented from leaking to the specified hydraulic line 9j.

  On the other hand, when the hydraulic pressure of the hydraulic oil chambers 5b, 5d of the second group is higher than the hydraulic pressure of the hydraulic oil chambers 5a, 5c of the first group and higher than the hydraulic pressure of the specified hydraulic line 9j, the second The hydraulic pressure in the hydraulic oil chambers 5b and 5d of the group pushes and opens the other check valve 10h and applies a check action to the one check valve 10g. This hydraulic pressure is applied to the hydraulic oil chambers 5a and 5c on the low pressure side. The leakage is prevented, and a check action is given to the pilot oil check valve 13b from the other end of the communication oil passage 10i through the pilot oil communication oil passage 13d, and this hydraulic pressure leaks to the specified hydraulic line 9j. prevent.

  Further, when the hydraulic oil chambers 5a, 5b, 5c, and 5d do not have sufficient hydraulic pressure necessary for the sealing action and the hydraulic pressure is lower than the hydraulic pressure of the specified hydraulic line 9j, the specified hydraulic line 9j. From the pilot oil inlet 13a to the pilot oil passage 13c pushes the pilot oil check valve 13b open and is supplied to the communication oil passage 10i through the pilot oil communication oil passage 13d. As in the first embodiment, the block-side and cover-side oil supply passages 10j, 12a communicate with the respective seals 2j, 2f, 2h, 3b, 1f to perform the sealing action, and the check valves 10g, 10h are non-returned. By acting, this hydraulic pressure is prevented from leaking to each hydraulic oil chamber 5a, 5b, 5c, 5d.

Furthermore, by making the oil hole 3j shown by the phantom line in FIG. 2 of the first embodiment, the vertical seal 1d of the segment 1b can also be sealed.
Therefore, even when the steering gear is unloaded or lightly loaded and the hydraulic pressure necessary for sealing is not generated in the hydraulic oil chambers 5a, 5b, 5c, 5d, at least the specified hydraulic line 9j Since the hydraulic pressure acts on each of the seals 2j, 2f, 2h, 3b, 1f, 1d, the sealing action is always performed with the hydraulic pressure exceeding the minimum required constant value, and in any state A reliable sealing action will be performed.

  In the third embodiment, as shown in the right side circuit of FIG. 10, when the control hydraulic pump 9g is not provided, the pilot oil inflow port 13a of the impulse valve block 13 is communicated with the specified hydraulic line 9j. However, as a hydraulic system to be communicated with the pilot oil inlet 13a, it is possible to communicate with a discharge side line of the hydraulic pump 9a instead of the specified hydraulic line 9j.

  In this case, when the direction switching valve 9b is in the switching position for sending the discharge oil from the hydraulic pump 9a to any of the hydraulic oil chambers (5a, 5c or 5b, 5d), the pilot oil inlet 13a has a hydraulic oil chamber. When the directional switching valve 9b is in the neutral position, that is, when the oil discharged from the hydraulic pump 9a is not sent to the hydraulic oil chambers 5a to 5d. The discharge hydraulic pressure of the hydraulic pump 9a defined by the pressure adjusting valve 9h acts on the pilot oil inlet 13a. Thereby, the object of the present invention can be achieved similarly.

  Next, a fourth embodiment of the present invention will be described with reference to FIGS. Note that members that perform basically the same operations as those described above with reference to FIG.

The vertical slit 2i includes a bottom surface S1 and a pair of side surfaces S2 and S3 facing each other in the circumferential direction of the rotor 2.
The vane 14 is divided into a vane body 14a and a seal retainer 14b. The vane body 14a is formed with an upper horizontal slit 2e, a lower horizontal slit 2g, and a bottom surface S1 and one side surface S2 of the vertical slit 2i. Further, the other end S3 facing the one side S2 of the vertical slit 2i is formed at the distal end of the seal holding member 14b in the radial direction, and the radius of the other side of the upper lateral slit 2e is formed above the sealing holding member 14b. A distal end portion in the direction is formed, and a distal end portion in the radial direction on the other side surface of the lower lateral slit 2g is formed in the lower portion of the seal restrainer 14b.

  The seal retainer 14b is detachably attached to the other side of the vane body 14a by a plurality of bolts 14c. As shown by the solid line in FIG. 12, in the state where the seal restrainer 14b is removed from the vane body 14a, the other side of the vertical slit 2i is opened, and the bottom surface S1 of the vertical slit 2i is opened from the other side of the vane body 14a. And one side S2 are completely exposed to the hydraulic oil chambers 5a to 5d. Further, as shown by the phantom line in FIG. 12, in the state where the seal restrainer 14b is attached to the vane body 14a, the vane 14 is formed with a vertical slit 2i composed of a pair of side surfaces S2, S3 and a bottom surface S1 facing each other. The

Hereinafter, the operation of the above-described configuration will be described.
In FIG. 1, when assembling the rotor 2 to the housing 1, with the seal retainer 14b removed from the vane body 14a, the lower lateral seal 2h is inserted into the lower lateral slit 2g of the vane body 14a. The rotor 2 is installed in the housing 1. In a state where the seal retainer 14b is removed from the vane body 14a, the other side of the vertical slit 2i is opened, and the bottom surface S1 and the one side surface S2 of the vertical slit 2i are exposed in the hydraulic oil chambers 5a to 5d. Therefore, using the space of the hydraulic oil chambers 5a to 5d, the vertical seal 2j is moved laterally from the other side where the vertical slit 2i is opened and inserted into the vertical slit 2i of the vane body 14a. Later, the seal retainer 14b is attached to the vane body 14a with bolts 14c. At this time, the skirt portion 2x of the vertical seal 2j is elastically compressed by the seal retainer 14b, and is in a properly inserted state. Thereafter, the upper horizontal seal 2f is inserted into the upper horizontal slit 2e from above.

  Accordingly, the vertical seal 2j can be easily and accurately attached to the vane 14 while visually confirming, and uneven distortion can be prevented from occurring in the vertical seal 2j. It can be visually confirmed whether or not the lower horizontal seal 2h is properly connected. Therefore, the difficulty in insertion work due to friction when the vertical seal 2j is pushed into the vertical slit 2i from above the vertical slit 2i while elastically compressing the skirt portion 2x as in the prior art is eliminated. In addition, non-uniform distortion of the vertical seal 2j caused by pushing in with elastic compression and various problems associated therewith are also eliminated, and the lower end of the vertical seal 2j is connected to the lower horizontal seal 2h. The problem of not being able to visually confirm whether or not they are properly connected is also solved.

  Further, when opening, after the seal retainer 14b is removed from the vane body 14a by the reverse procedure, the vertical seal 2j is taken out from the circumferential direction into the space of the hydraulic oil chambers 5a to 5d. As a result, it is difficult to pull the vertical seal 2j upward due to the frictional resistance between the skirt portion 2x of the vertical seal 2j and the vertical slit 2i as in the prior art, and this causes damage to the vertical seal 2j. The potential problem is solved.

  In the above embodiment, the rotor 2 is built in the housing 1 after the lower horizontal seal 2h is first inserted into the lower horizontal slit 2g. However, in the state where the seal restrainer 14b is removed from the vane body 14a. Since the tip of the lower horizontal slit 2g in the radial direction is exposed in the space of the hydraulic oil chambers 5a to 5d, the longitudinal seal 2j is inserted after the rotor 2 is installed in the housing 1 using this exposed portion. In addition, the lower horizontal seal 2h can be bent in the circumferential direction and inserted into the lower horizontal slit 2g. As a result, there is no possibility of the natural dropout of the lower horizontal seal 2h during operation, which can be considered when the rotor 2 is assembled in the housing 1 with the lower horizontal seal 2h inserted in the lower horizontal slit 2g. In addition, when opening / inspecting the lower horizontal seal 2h, it is necessary to remove the lower horizontal seal 2h by removing the coupling between the rotor 2 and the rudder shaft and pulling up the rotor 2 as in the past. The problem of becoming is also solved.

  The above-described embodiment relating to the installation of the vertical seal 2j of the vane 14 can also be applied to the installation of the vertical seal 1d of the segment 1b. Since the configuration and operation are the same as those of the above-described embodiment for the vane 14, the description thereof is omitted.

  Next, a fifth embodiment of the present invention will be described with reference to FIGS. Note that members that perform basically the same operations as those described above with reference to FIG.

  As shown in FIGS. 1, 13, and 14, the upper end surface 15 d of the vertical seal 15 c of the vane 2 d abuts on the bottom surface 15 e (that is, the back surface) on the radially outer end side of the upper horizontal seal 15 a on the flat surface, and the vertical seal The lower end surface 15f of 15c contacts the upper surface 15g (that is, the back surface) on the radially outer end side of the lower horizontal seal 15b on a flat surface.

  The cross-sectional shape of the vertical seal 15c is the same as that shown in FIG. 30, and protrudes from both sides of the base portion 15h and the back surface (inner end surface) of the base portion 15h toward the back side of the vertical slit 2i and in the circumferential direction. It is comprised from a pair of skirt part 15i which opposes, and has comprised uniform cross-sectional shape over the full length of the vertical direction.

  As shown in FIG. 14, the bottom surface 15j of the upper horizontal seal 15a is provided with a recess 15k and ridges 15m, 15n, 15o surrounding the periphery of the recess 15k. The upper horizontal seal 15a is constituted by the recess 15k, the bank portions 15m, 15n, and 15o and the base portion 15p formed thereabove.

  The depth of the recess 15k is substantially the same as the depth of the skirt portion 15i of the vertical seal 15c. Further, the pair of bank portions 15m and the bank portion 15n on the radially inner end side that are opposed to each other in the circumferential direction of the rotor 2 have substantially the same thickness as the cross-sectional thickness of the skirt portion 15i of the vertical seal 15c. Yes. In addition, the bank portion 15o on the outer end side in the radial direction is formed flat and has substantially the same thickness as the radial thickness in the cross section of the base portion 15h of the vertical seal 15c. In addition, as in the case of the skirt portion 15i of the vertical seal 15c, the distal ends of both the bank portions 15m of the upper horizontal seal 15a are slightly more than the side surfaces of the base portion 15p in the free state before being attached to the upper horizontal slit 2e. Projecting outward in the circumferential direction.

  In a state where the upper horizontal seal 15a is connected to the vertical seal 15c, the space between the skirt portions 15i of the vertical seal 15c and the recess 15k of the upper horizontal seal 15a communicate with each other. The longitudinal lengths of the upper and lower horizontal seals 15a and 15b and the vertical seal 15c should be kept oiltight between each end surface and the mating surface even at a low temperature in the initial stage of operation after insertion. In order to be able to do this, the free length is determined so that a certain amount of elastic compression is performed when inserting from the free state.

  Further, the lower horizontal seal 15b is the same structure as the upper horizontal seal 15a, and is inverted up and down. The same reference numerals as those for the upper horizontal seal 15a are given with dashes, and the description thereof is omitted.

Hereinafter, the operation of the above-described configuration will be described.
When assembling the rotor 2 to the housing 1, first, the lower side seal 15b is moved into the lower side slit 2g of the vane 2d by compressing the tips of both ridges 15m 'of the lower side seal 15b toward each other. Insert it.

  Then, after the rotor 2 is inserted into the housing 1, the vertical seal 15c is inserted from the top opening of the vertical slit 2i of the vane 2d while the tips of both skirt portions 15i of the vertical seal 15c are compressed in the direction approaching each other. .

  Finally, the top horizontal seal 15a is compressed by compressing the tips of both ridges 15m of the upper horizontal seal 15a toward each other and applying a slight elastic compression in the longitudinal direction of the upper horizontal seal 15a. Insert into 2e.

  In this state, the distal end in the radial direction of the upper horizontal seal 15a is raised by an amount that the free length before the vertical seal 15c is slightly longer than the length after the vertical seal 15c is mounted. This swell is compressed by assembling the top cover 3 to the housing 1, whereby appropriate initial contact with the connecting surfaces of the upper and lower end faces 15 d and 15 f of the vertical seal 15 c and the upper and lower horizontal seals 15 a and 15 b. A surface pressure is generated, and oil tightness is secured at these connecting surfaces.

  In this state, when the hydraulic oil from the hydraulic oil chambers 5a to 5d or from the hydraulic system is guided to the space between the skirt portions 15i of the vertical seal 15c through the rotor sealing oil hole 11b, the hydraulic pressure is The seal surface of the vertical seal 15c is pressed against the inner peripheral surface of the housing 1 which is the mating surface to keep the hydraulic oil chambers 5a to 5d tight and the skirt portions 15i are pressed against both side surfaces of the vertical slit 2i. Prevents hydraulic fluid from leaking to the low pressure side.

  Further, the pressure oil is communicated from the vertical seal 15c to the upper and lower horizontal seals 15a, 15b by communication between the space between the skirts 15i of the vertical seal 15c and the recesses 15k, 15k 'of the upper and lower horizontal seals 15a, 15b. Acting on the respective recesses 15k, 15k ′ of 15b, the respective seal surfaces of the upper and lower lateral seals 15a, 15b are pressed against the back surface of the top cover 3 and the inner bottom surface of the housing 1 as mating surfaces, respectively, 15m, 15m ′, 15n, and 15n ′ are pressed against the respective side surfaces of the upper and lower lateral slits 2e and 2g to prevent leakage of high-pressure hydraulic oil from this portion to the low-pressure side.

  In the configuration and operation described above, it is not necessary to provide a pressure valve across the vane 2d as in the prior art. Further, the upper end surface 15d of the vertical seal 15c abuts on the bottom surface 15e of the bank portion 15o of the upper horizontal seal 15a, and the lower end surface 15f of the vertical seal 15c contacts the upper surface 15g of the bank portion 15o ′ of the lower horizontal seal 15b. The upper and lower end faces 15d, 15f of the vertical seal 15c and the upper and lower horizontal seals 15a, 15b are connected by contact of flat surfaces. Therefore, due to the difference in elastic compression and thermal expansion between the vertical seal 15c and the horizontal seals 15a and 15b, the contact surface pressure of the connecting portion, the outer end surfaces of the horizontal seals 15a and 15b, and the housing 1 And the contact surface pressure between the inner end surface of each of the horizontal seals 15a and 15b and the inner end surface of the lateral slits 2e and 2g are improperly affected. Things will disappear. In addition, the connection between the vertical seal 15c and the lower horizontal seal 15b is naturally appropriate in spite of the fact that the work is not visible.

  Further, conventionally, when the top cover 3 is attached and each of the seals 2f, 2h, 2j is elastically compressed, it cannot be visually checked, so that the vertical seal 2j and the upper and lower horizontal seals 2f, 2h are connected to each other. Although abnormal deformation may occur, the above embodiment can prevent such abnormal deformation from occurring in the connecting portion.

  Therefore, these prevent the high pressure hydraulic fluid from leaking to the low pressure side from the connecting portion between the vertical seal 15c and the upper and lower horizontal seals 15a, 15b. Abnormal wear of the seals 15a, 15b, 15c is also avoided.

  In addition, as shown in FIG. 15, in the bank portions 15m and 15m ′ of the upper and lower horizontal seals 15a and 15b, the recesses 15k and 15k ′ are formed at the boundaries between the bank portions 15n and 15n ′ and the bank portions 15o and 15o ′. , 15k ′ may be provided with a cut 15q.

  According to this, since the cut 15q is provided, the bank portions 15m and 15m ′ and the bank portions 15n and 15n ′ can be individually deformed inward and outward. Therefore, when the pressure oil acts in the recesses 15k and 15k ′, the bank portions 15m and 15m ′ and the bank portions 15n and 15n ′ are uniformly pressed against the side surfaces of the upper and lower horizontal slits 2e and 2g, Leakage of oil to the low pressure side can be prevented more reliably.

  Next, a sixth embodiment of the present invention will be described with reference to FIGS. Note that members that perform basically the same operations as those described above with reference to FIG.

  On the upper surface of the vane 2d, a pair of upper left and right lateral slits 16a, 17a facing each other in the circumferential direction of the rotor 2 are formed facing the back surface of the top cover 3. In addition, a pair of lower left and right lateral slits 16 b and 17 b facing each other in the circumferential direction are formed on the lower surface of the vane 2 d so as to face the inner bottom surface of the housing 1. Further, a pair of left and right vertical slits 16 c and 17 c that are opposed to each other in the circumferential direction are formed on the distal end surface in the radial direction of the vane 2 d so as to face the inner circumferential surface of the housing 1. The upper ends of the left and right vertical slits 16c and 17c communicate with the outer ends in the radial direction of the upper left and right horizontal slits 16a and 17a, and the lower ends of the left and right vertical slits 16c and 17c are in the radial direction of the lower left and right horizontal slits 16b and 17b. It communicates with the outer end.

  Upper left and right horizontal seals 16d and 17d made of an elastic material are held in the upper left and right horizontal slits 16a and 17a, respectively. The seal surfaces 16e and 17e of the upper left and right lateral seals 16d and 17d are slidably contacted with the back surface of the top cover 3, and the radially outer end surfaces 16f and 17f are slidably contacted with the inner peripheral surface of the housing 1 and each radially inner end surface 16g. , 17g are in sliding contact with the lower peripheral edge of the upper ring seal 3b.

  Lower left and right horizontal seals 16h and 17h made of an elastic material are held in the lower left and right horizontal slits 16b and 17b, respectively. The seal surfaces 16i and 17i of the lower left and right lateral seals 16h and 17h are in sliding contact with the inner bottom surface of the housing 1, and the radial outer end surfaces 16j and 17j are in sliding contact with the inner peripheral surface of the housing 1, and the radial inner end surfaces 16k. , 17k are in sliding contact with the upper peripheral edge of the lower ring seal 1f.

  A left vertical seal 16l made of an elastic material is sandwiched in the left vertical slit 16c, and is disposed between the radial outer end of the upper left horizontal seal 16d and the radial outer end of the lower left horizontal seal 16h. Yes. A right vertical seal 17l made of an elastic material is sandwiched in the right vertical slit 17c, and is disposed between the radial outer end of the upper right horizontal seal 17d and the radial outer end of the lower right horizontal seal 17h. Has been. The contact between the left horizontal seals 16d and 16h and the upper and lower ends of the left vertical seal 16l and the contact between the right horizontal seals 17d and 17h and the upper and lower ends of the right vertical seal 17l are both flat surfaces. It is.

  As shown in FIG. 17, the horizontal cross sections of the left and right vertical seals 16l and 17l are arranged so as to maintain a line-symmetric relationship with respect to the radial straight line L1 passing between the left and right vertical seals 16l and 17l. As shown in FIG. 17, the left and right vertical seals 16 l and 17 l are respectively defined as bases 16 m and 17 m disposed near the straight line L 1, and the straight line L 1 along the circumferential direction of the rotor 2 from the bases 16 m and 17 m. The first lips 16n and 17n and the second lips 16o and 17o project in the opposite direction.

  The tip portions P1 of the first lips 16n and 17n are in sliding contact with the inner peripheral surface of the housing 1 in the assembled state (see FIG. 17), and in the free state where they are removed from the left and right vertical slits 16c and 17c. It protrudes outward in the radial direction from the outer end surface in the radial direction (see FIG. 18). Further, a slight gap D1 is formed between the front end portion P1 of the first lips 16n and 17n and the outer side surfaces of the left and right vertical slits 16c and 17c.

  The second lips 16o, 17o are formed on the inner side in the radial direction than the first lips 16n, 17n. The distal end portion P2 of the second lips 16o, 17o abuts on the outer side surface of the left and right vertical slits 16c, 17c in the assembled state, and in the radial direction of the base portions 16m, 17m in the free state where the second lips 16o, 17o are removed from the left and right vertical slits 16c, 17c It protrudes slightly inward in the radial direction from the inner tip surface (see FIG. 18). The left and right vertical seals 16l and 17l form oil grooves 16p and 17p surrounded by the inner peripheral surface of the housing 1, the base portions 16m and 17m, and the first lips 16n and 17n.

The upper left and right horizontal seals 16d and 17d and the lower left and right horizontal seals 16h and 17h are arranged symmetrically in the vertical direction, but the configurations are all the same.
That is, the upper left and right lateral seals 16d and 17d have base portions 16w and 17w, respectively, and the bottom surfaces 16q and 17q (that is, the back surface) surround the recesses 16s and 17s and the periphery of the recesses 16s and 17s. It has formed bank portions 16u and 17u.

  Similarly, the lower left and right lateral seals 16h and 17h have base portions 16x and 17x, respectively, and surround the recesses 16t and 17t on the upper surfaces 16r and 17r (that is, the back surface) and the periphery of the recesses 16t and 17t. And the bank portions 16v and 17v.

  The bank portions 16u, 17u, 16v, and 17v have base portions 16w, 17w, 16x, and 17x in a free state in which the horizontal seals 16d, 17d, 16h, and 17h are removed from the horizontal slits 16a, 17a, 16b, and 17b, respectively. It protrudes slightly outward in the circumferential direction.

  As shown in FIGS. 16 and 17, in the state where the horizontal seals 16d, 17d, 16h, and 17h are connected to the vertical seals 16l and 17l, outer end portions in the radial direction of the recesses 16s, 17s, 16t, and 17t, respectively. Communicates with the gap D2 (see FIG. 18) between the first lips 16n, 17n and the second lips 16o, 17o of the vertical seals 16l, 17l.

  The longitudinal lengths of the horizontal seals 16d, 17d, 16h, and 17h and the vertical seals 16l and 17l are the oils between the end surfaces and the mating surfaces even in the low-temperature state at the initial stage of operation after insertion. In order to be able to maintain a high density, the free length is determined so that a certain amount of elastic compression is performed when inserting from a free state.

Hereinafter, the operation of the above-described configuration will be described.
When assembling the rotor 2 to the housing 1, first, the tip portions of the pair of bank portions 16v and 17v facing each other in the circumferential direction of the lower left and right horizontal seals 16h and 17h are compressed in the direction of approaching each other, 16h and 17h are inserted into the lower left and right horizontal slits 16b and 17b of the vane 2d, respectively.

  And after inserting the rotor 2 in the housing 1, the front-end | tip part P1 of the 1st lips 16n and 17n of the left-right vertical seals 16l and 17l and the front-end | tip part P2 of the 2nd lips 16o and 17o approach mutually. The left and right vertical seals 16l and 17l are inserted from the top openings of the left and right vertical slits 16c and 17c of the vane 2d while being compressed in each direction. In this state, the front end portions P1 of the first lips 16n and 17n are in contact with the inner peripheral surface of the housing 1 with an appropriate contact surface pressure, and the front end portions P2 of the second lips 16o and 17o are left and right vertical slits 16c, It contacts the bottom surface of 17c with an appropriate contact surface pressure.

  Finally, the tip portions of the pair of bank portions 16u and 17u facing each other in the circumferential direction of the upper left and right horizontal seals 16d and 17d are compressed in the direction of approaching each other, and slightly in the longitudinal direction of the upper left and right horizontal seals 16d and 17d. Applying elastic compression, the upper left and right horizontal seals 16d and 17d are inserted into the upper left and right horizontal slits 16a and 17a.

  In this state, the outer ends in the radial direction of the upper left and right horizontal seals 16d and 17d are raised by the amount that the free length before mounting of the left and right vertical seals 16l and 17l is slightly longer than the length after mounting. This swell is compressed by assembling the top cover 3 to the housing 1, whereby the upper and lower end faces of the left and right vertical seals 16l and 17l and the connecting surfaces of the upper and lower left and right horizontal seals 16d, 17d, 16h and 17h, respectively. Therefore, an appropriate initial contact surface pressure is generated, and oil tightness is secured on these connecting surfaces.

  In this state, for example, if the hydraulic oil chamber 5a (or 5c) facing the right vertical seal 17l is in a high pressure state, the pressure oil in the hydraulic oil chamber 5a passes through the gap D1 and passes through the right vertical seal 17l. Enters the gap D2 between the first lip 17n and the second lip 17o. The first lip 17n is pressed against the inner peripheral surface of the housing 1 by the hydraulic pressure acting on the gap D2 at this time, and the second lip 17o is pressed against the bottom surface of the right vertical slit 17c, and the hydraulic oil chamber 5a (or 5c). The internal high-pressure hydraulic oil is prevented from leaking to the adjacent low-pressure hydraulic oil chamber 5d (or 5b) along the bottom surfaces of the right vertical seal 17l and the right vertical slit 17c.

  Further, since the high-pressure hydraulic oil that has entered the gap D2 of the right vertical seal 17l also enters the respective recesses 17s and 17t of the upper and lower right side seals 17d and 17h from the gap D2, the upper and lower right oil The seal surfaces 17e and 17i of the horizontal seals 17d and 17h are pressed against the back surface of the top cover 3 and the inner bottom surface of the housing 1 as mating surfaces, respectively, and the bank portions 17u and 17v are respectively pressed into the upper and lower right side slits 17a and 17b. To prevent leakage of high pressure hydraulic oil from this part to the low pressure side.

  On the contrary, when the hydraulic oil chamber 5d (or 5b) on the left vertical seal 16l side is in a high pressure state, the high-pressure hydraulic oil in the hydraulic oil chamber 5a (or 5c) described above is transferred to the upper part of the right vertical seal 17l. High pressure hydraulic oil in the hydraulic oil chamber 5d (or 5b) acts on the left vertical seal 16l and the upper and lower left horizontal seals 16d, 16h by the same action as it acts on the lower right horizontal seals 17d, 17h. Prevent leakage of hydraulic fluid from the high pressure side to the low pressure side.

  In the above-described configuration and operation, it is not necessary to introduce the pressure oil from the high-pressure hydraulic oil chambers 5a to 5d through the separate oil passages to the back surfaces of the left and right vertical seals 16l and 17l, and cross the rotor vane 2d. There is no need to provide a pressure valve.

  Further, when the hydraulic oil chambers 5a, 5c are in a high pressure state, the high pressure hydraulic oil acts on the right seals 17d, 17h, 17l, does not act on the left seals 16d, 16h, 16l, When the hydraulic oil chambers 5d and 5b are in a high pressure state, the high pressure hydraulic oil acts on the left seals 16d, 16h, and 16l, and does not act on the right seals 17d, 17h, and 17l. Accordingly, since the time for operating the respective seals 16d, 16h, 16l, 17d, 17h, and 17l under the action of the high-pressure hydraulic oil is halved, the respective seals 16d, 16h, 16l, 17d, 17h, and 17l. This has the effect of theoretically doubling the lifetime.

  Further, the upper end surfaces of the left and right vertical seals 16l and 17l and the upper left and right horizontal seals 16d and 17d are connected by flat surfaces, and the lower end surfaces of the left and right vertical seals 16l and 17l and the lower left and right horizontal seals 16h and 17h are flat. Since the surfaces are connected to each other, as in the case of the fifth embodiment, when the vertical seals 16l and 17l and the horizontal seals 16d, 17d, 16h and 17h are applied with initial elastic compression, In particular, in the connection of the lower left and right horizontal seals 16h and 17h and the left and right vertical seals 16l and 17l, which is an operation in an invisible state, to prevent abnormal deformation of the connection portion and inappropriate influence on the contact surface pressure. Therefore, leakage of hydraulic fluid and abnormal wear of the seal are avoided.

  As in the case of the fifth embodiment described above with reference to FIG. 15, the upper and lower left and right lateral seals 16d, 17d, 16h, and 17h are arranged in the radial direction of the bank portions 16u, 17u, 16v, and 17v. You may provide the cut | interruption which reaches the bottom face of the pits 16s, 17s, 16t, and 17t in both ends.

  According to this, when the pressure oil acts on the recesses 16s, 17s, 16t, 17t, the pressing of the lateral slits 16a, 17a, 16b, 17b on the side portions 16u, 17u, 16v, 17v becomes more uniform, Leakage of the pressure oil to the low pressure side at this portion can be prevented more reliably.

  In the configuration and operation described above, it is not necessary to separately introduce the pressure oil to the back surface of each seal of the vane 2d. Therefore, in each of the previous embodiments, the operation as described with reference to FIGS. A pressure oil supply system from the oil chambers 5a to 5d, from the control hydraulic line 9i of the control hydraulic pump 9g, or from the specified hydraulic line 9j to the back of each seal of the vane 2d becomes unnecessary.

  Further, if the vertical seal of the segment 1b is configured as shown in claim 6 of, for example, Japanese Patent Application Laid-Open No. 2003-161371 “Sealing structure of a rotary vane type steering machine”, a pressure oil supply system that similarly reaches the back of the seal Is no longer necessary. However, the upper and lower ring seals 3b and 1f still need to guide the pressure oil to their rear surfaces 3e and 1n. In this case, the following configuration is used.

  That is, as shown in FIG. 19, the top cover 3 is perforated with an oil passage 3k that communicates from the upper surface to the back surface 3e of the upper ring seal 3b, and the housing 1 communicates from the lower surface to the back surface 1n of the lower ring seal 1f. The oil passage 1r to be drilled is drilled.

  Further, as shown in FIG. 20, with respect to the anti-shock valve block 13, the pressure oil extraction port 10k and the block-side oil supply passage 10j shown in FIGS. A pressure oil extraction port 10l is formed on the other side of the block 13, and the other end of the communication oil passage 10i is extended to communicate with the pressure oil extraction port 10l. As shown in FIG. 19, the pressure oil extraction port 10 l and both the oil passages 3 k and 1 r are communicated with each other through a communication oil pipe L.

  As a result, the higher hydraulic pressure of the hydraulic oil chambers 5a, 5c or the hydraulic oil chambers 5b, 5d opens one of the check valves 10g, 10h, passes through the communication oil passage 10i, and passes through the pressure oil extraction port 10l. It always acts on the back surfaces 3e, 1n of the upper and lower ring seals 3b, 1f through the oil passages 3k, 1r via the communication oil pipe L. Thereby, the sealing action of the upper and lower ring seals 3b and 1f can be ensured.

  Further, as shown in FIG. 21, the anti-impact valve block 13 is connected to the pilot oil inlet 13a, the pilot oil check valve 13b, the pilot oil passage 13c, and the pilot oil shown in FIGS. A communication oil passage 13d may be provided.

  According to this, when the higher hydraulic pressure of the hydraulic oil chambers 5a, 5c or the hydraulic oil chambers 5b, 5d reaches a sufficient hydraulic pressure necessary for sealing, the hydraulic oil chambers 5a, 5c or the hydraulic oil chamber 5b, The higher hydraulic pressure of 5d acts on the back surfaces 3e and 1n of the upper and lower ring seals 3b and 1f, respectively.

  Further, when sufficient hydraulic pressure necessary for sealing is not generated in each of the hydraulic oil chambers 5a to 5d, as shown in the left half of FIG. 10, the hydraulic pressure of the control hydraulic line 9i of the control hydraulic pump 9g or the right half of FIG. As shown in FIG. 4, any of the hydraulic pressures in the specified hydraulic line 9j passes through the pilot oil inlet 13a through the pilot oil passage 13c, opens the pilot oil check valve 13b, and supplies the pilot oil communication oil passage 13d to the communication oil passage 10i. Is done. Thereby, the back surface 3e of each of the upper and lower ring seals 3b, 1f is set so that the hydraulic pressure of the control hydraulic line 9i of the control hydraulic pump 9g is the minimum pressure or the hydraulic pressure of the specified hydraulic line 9j is the minimum pressure. Acts on 1n. Thereby, even if the hydraulic pressure in each of the hydraulic oil chambers 5a to 5d is insufficient, the sealing action of the upper and lower ring seals 3b and 1f can be ensured.

  Next, a seventh embodiment of the present invention will be described with reference to FIGS. Members that perform basically the same operations as those described above with reference to FIGS. 13 and 14 are assigned the same reference numerals and description thereof is omitted.

  As shown in FIG. 22, the vane 18 is formed as a bent portion 18c in which the lower corner portion of the tip end surface 18b is curved in an arc shape. Accordingly, the inner peripheral surface of the housing 18d is also formed as an arcuate bent portion 18e whose lower corner is opposed to the bent portion 18c of the vane 18.

  An upper horizontal slit 2e is formed on the upper end surface of the vane 18, and an upper horizontal seal 15a that is in sliding contact with the back surface of the top cover 3 is inserted into the upper horizontal slit 2e. A bent slit 18f is formed in the vane 18 from the tip end surface 18b of the vane 18 through the bent portion 18c to the radial end surface of the lower end of the rotor 2 (lower end outer peripheral surface of the rotor 2). The curved slit 18f is composed of a bottom surface S1 and a pair of side surfaces S2 and S3 facing each other in the circumferential direction of the rotor 2. A bending seal 18g that is in sliding contact with the inner peripheral surface and the inner bottom surface of the housing 18d is inserted into the bending slit 18f. The seals 15a and 18g are made of an elastic material.

  The upper horizontal seal 15a has the same configuration as that described in the previous embodiment. Further, the upper end surface 18h of the bent seal 18g and the bottom surface 15e on the radially outer end side of the upper horizontal seal 15a are formed flat, and the upper end surface 18h and the bottom surface 15e are brought into contact with each other by the contact between the flat surfaces. And are connected. Further, the lower edge of the lower end face 18i of the bent seal 18g is in contact with the outer peripheral edge 1i of the lower ring seal 1f.

  The cross sectional shape of the bent seal 18g is the same as that of the vertical seal 15c shown in FIG. 14, and is composed of a base portion 18j and a skirt portion 18k, and has a uniform cross sectional shape over the entire length in the longitudinal direction.

  As shown in FIGS. 24 and 25, the vane 18 is divided into a vane body 18a and a seal retainer 18n. The vane body 18a is formed with an upper horizontal slit 2e, a bottom surface S1 and a side surface S2 of the vertical portion of the bent slit 18f, and a lower side horizontal portion of the bent slit 18f. Further, the other end S3 opposite to the one side S2 of the curved slit 18f is formed at the distal end in the radial direction of the seal retainer 18n, and the radius of the other side of the upper lateral slit 2e is formed above the seal retainer 18n. A directional tip is formed.

  The seal restrainer 18n is detachably attached to the other side of the vane body 18a by a plurality of bolts 18o. As shown by the solid line in FIG. 25, when the seal restrainer 18n is removed from the vane body 18a, the other sides of the bent slit 18f and the bent portion are opened, and the other side of the vane body 18a is opened. From the side, the bottom surface S1 and one side surface S2 of the curved slit 18f are completely exposed to the hydraulic oil chambers 5a to 5d. Further, as shown by the phantom line in FIG. 25, when the seal restrainer 18n is attached to the vane main body 18a, the vane 18 is formed with a curved slit 18f composed of a pair of side surfaces S2, S3 and a bottom surface S1. Is done.

Hereinafter, the operation of the above-described configuration will be described.
When the rotor 2 is assembled to the housing 1, as shown by the solid line in FIG. 25, the rotor 2 is housed in the housing 1 with the seal restrainer 18n removed from the vane body 18a. In a state in which the seal retainer 18n is removed from the vane body 18a, the other side of the bent slit 18f and the bent portion are opened, and the bottom surface S1 of the bent slit 18f is flush with the bottom surface S1. The side surface S2 is exposed to the hydraulic oil chambers 5a to 5d. For this reason, using the space of the hydraulic oil chambers 5a to 5d, first, the bent slit 18f is bent from the exposed portion of the bent portion of the bent slit 18f while bending the lower end portion of the bent seal 18g in the circumferential direction. It inserts into the lower end horizontal part of 18f, and after that, the bending part and vertical part of the bending seal 18g are inserted into the bending slit 18f from the other open side.

  Thereafter, as shown by phantom lines in FIGS. 24 and 25, the seal restrainer 18n is attached to the vane body 18a with bolts 18o. At this time, the bent seal 18g has a skirt portion 18k that is elastically compressed by the seal restrainer 18n, and is in a properly inserted state. Thereafter, the upper horizontal seal 15a is inserted into the upper horizontal slit 2e from above.

  In the operating state of the vane 18, the hydraulic oil from the hydraulic oil chambers 5a to 5d or the hydraulic system is guided to the space between the skirt portions 18k of the curved seal 18g through the rotor sealing oil hole 11b. The base 18j is pushed from the back side of the bent seal 18g, and the seal surface is pushed against the inner peripheral surface and the inner bottom surface of the housing 18d, which is the mating surface, to ensure the oil tightness of the hydraulic oil chambers 5a to 5d, and both skirts The portion 18k is pressed against both side surfaces S2, S3 of the curved slit 18f to prevent leakage of the high pressure hydraulic oil from this portion to the low pressure side.

The hydraulic pressure is supplied from the back side of the curved seal 18g to the recess 15k of the upper lateral seal 15a, and performs exactly the same action as described in the previous embodiment.
Thus, the bent seal 18g can be easily and accurately attached to the vane 18 while visually confirming during the seal installation and opening inspection work. Therefore, since the conventional vertical seal 2j and the lower horizontal seal 2h are not connected, the conventional problems associated therewith are solved. Furthermore, various problems that occur because the connecting portion between the vertical seal 2j and the lower horizontal seal 2h cannot be visually confirmed in the prior art are also solved, and the vane 18 can be lifted without lifting the rotor 2 off the rudder shaft. Open inspection of the seal can be performed.

Next, an eighth embodiment of the present invention will be described with reference to FIG.
The seal 19a has a base portion 19b and a pair of skirt portions 19c protruding from both side portions of the base portion 19b to the back side, and is inserted into the slit 19d. The vertical seal (2j, 15c) and the curved seal (18g) in the above-described embodiment are applied as the seal 19a, and the vertical slit (in the above-described embodiment is used as the slit 19d. 2i) and the curved slit (18f) are applied.

  The seal surface 19e of the base 19b is in sliding contact with the mating sliding contact surface 19f while moving in the rotation direction of the rotor 2. As the sliding contact surface 19f, the inner peripheral surface or inner bottom surface of the housing 1 or the back surface of the top cover 3 in the above-described embodiment is applied.

  The tips of both skirt portions 19c slightly protrude outward from both side surfaces of the base portion 19b in a free state in which the seal 19a is removed from the slit 19d. An oil groove 19g is formed in the longitudinal direction in the central portion in the circumferential direction (rotational direction of the rotor 2) or radial direction of the seal surface 19e of the base portion 19b. A fine oil hole 19h communicating with the bottom of the oil groove 19g and the space between the skirt portions 19c is formed in the base portion 19b. A sealing oil hole 19i communicating with the hydraulic oil chambers 5a to 5d or the hydraulic circuit is provided at the bottom of the slit 19d.

Hereinafter, the operation of the above-described configuration will be described.
The hydraulic fluid guided from the hydraulic fluid chambers 5a to 5d or the hydraulic circuit enters the bottom of the slit 19d through the sealing oil hole 19i, presses the back surface of the seal 19a with hydraulic pressure, and the seal surface 19e against the mating sliding surface 19f. To exert the sealing action in this part. At the same time, the hydraulic pressure presses both the skirt portions 19c against both side surfaces of the slit 19d and prevents the high pressure hydraulic oil from leaking to the low pressure side through these portions. A small amount of hydraulic oil is always supplied to the oil groove 19g from the space between the skirt portions 19c through the fine oil hole 19h.

  For example, when the rotor 2 rotates counterclockwise and the sealing surface 19e of the base portion 19b slides in the left direction F with respect to the mating sliding contact surface 19f, the left edge i of the sealing surface 19e is scraper against the oil. In this way, the lubrication by the hydraulic oil between the seal surface 19e and the mating sliding contact surface 19f is broken. However, since the oil groove 19g is filled with the hydraulic oil, the oil on the subsequent seal surface 19e The portion B on the right side of the groove 19g is prevented from sliding without lubrication, and the portion B on the right side of the oil groove 19g on the seal surface 19e is ensured. Similarly, when the rotor 2 rotates to the right and the seal surface 19e of the base portion 19b slides in the right direction with respect to the slidable contact surface 19f, the portion on the left side of the oil groove 19g of the seal surface 19e is also the same. It is possible to avoid sliding without lubrication. Therefore, it is possible to prevent the sliding in the state without lubrication due to the scraper action and the promotion of the wear due to the scraper action, which has been a problem in the past.

  In the eighth embodiment, the seal 19a is applied to the vertical seals 2j and 15c and the curved seal 18g in the above-described embodiment. However, the upper and lower horizontal seals 2f, 2h, 15a, 15b, It can also be applied to 16d, 17d, 16h, and 17h, and exhibits the same effect. In this case, the oil groove 19g is provided at the center in the circumferential direction of the seal surface and extends in the longitudinal direction, and communicates with the bottom of the oil groove 19g and the recesses 15k, 15k ′, 16s, 17s, 16t, and 17t on the back side. A fine oil hole 19h is provided in the base. Further, as the sliding contact surface 19f, the inner bottom surface of the housing 1 or the back surface of the top cover 3 in the above-described embodiment is applied.

  Further, in each of the upper and lower lateral seals 2f, 2h, 15a, 15b, 16d, 17d, 16h, 17h, in addition to the oil groove 19g in the longitudinal direction of the seal surface communicating with the fine oil hole 19h in the base, A thickness direction (in the thickness direction) that communicates with the oil groove 19g on the radially outer peripheral side end surfaces of the upper and lower lateral seals 2f, 2h, 15a, 15b, 16d, 17d, 16h, and 17h that are in sliding contact with the inner peripheral surface of the housing 1. You may form the outer end part oil groove of an up-down direction.

  In this case, the sliding in the absence of lubrication due to the scraper action and the acceleration of the wear are similarly applied to the radially outer end faces of the horizontal seals 2f, 2h, 15a, 15b, 16d, 17d, 16h, and 17h. Can be prevented.

It is a whole longitudinal cross-sectional view which shows the rotary vane type steering machine in the 1st Embodiment of this invention. It is a detailed sectional view of the A section in FIG. It is a detailed sectional view of the B section in FIG. FIG. 6 is a cross-sectional view of an anti-vibration valve block of the rotary vane type steering machine, and is a cross-sectional view taken along the line aa in FIG. 5. It is a top view of the anti-shock valve block of a rotary vane type steering machine. FIG. 6 is a cross-sectional view of the anti-vibration valve block of the rotary vane type steering machine, and is a cross-sectional view taken along the line bb in FIG. 5. It is sectional drawing of the anti-shock valve block of the rotary vane type steering machine in the 2nd Embodiment of this invention, and is cc arrow sectional drawing in FIG. It is a top view of the anti-shock valve block of a rotary vane type steering machine. FIG. 9 is a cross-sectional view of an anti-vibration valve block of the rotary vane type steering machine, and is a cross-sectional view taken along the line dd in FIG. 8. It is a figure which shows the hydraulic circuit of a rotary vane type steering machine. It is a perspective view of the vane of the rotary vane type steering machine in the 4th Embodiment of this invention. It is XX arrow sectional drawing in FIG. It is a longitudinal cross-sectional view of the vane of the rotary vane type steering machine in the 5th Embodiment of this invention. It is an ee arrow line view in FIG. It is a figure of the back side of the upper and lower horizontal seal provided in the vane of a rotary vane type steering machine. It is a longitudinal cross-sectional view of the vane of the rotary vane type steering machine in the 6th Embodiment of this invention. It is ff arrow sectional drawing in FIG. It is an enlarged horizontal sectional view which shows the shape in the free state of the vertical seal | sticker provided in the vane of the rotary vane type steering machine. It is the whole longitudinal cross-sectional view of a rotary vane type steering machine. It is a longitudinal cross-sectional view of the impact valve block of a rotary vane type steering machine. FIG. 21 is a longitudinal sectional view of an anti-vibration valve block of the rotary vane type steering machine, which is obtained by adding pilot oil introducing means to FIG. 20. It is a longitudinal cross-sectional view of the vane of the rotary vane type steering machine in the 7th Embodiment of this invention. It is a gg arrow line view in FIG. It is a side view of the vane. It is a XX arrow line view in FIG. It is a horizontal sectional view which shows the vertical seal | sticker of the rotary vane type steering machine in the 8th Embodiment of this invention. It is a whole longitudinal cross-sectional view which shows the conventional rotary vane type steering machine, and is a hh arrow longitudinal cross-section in FIG. It is a partially cutaway perspective view of the rotary vane type steering machine. It is a horizontal sectional view of the whole rotary vane type steering machine. It is a horizontal sectional view in the free state of the vertical and horizontal seal of the vane of the rotary vane type steering machine and the vertical seal of the segment. It is an enlarged vertical sectional view in the free state of the ring seal of a rotary vane type steering machine. It is a perspective view of the upper part of the vane of a rotary vane type steering machine. It is ii arrow sectional drawing in FIG. It is j arrow sectional drawing in FIG. It is kk arrow sectional drawing in FIG. It is a horizontal sectional view of the pressure valve provided in the vane of the rotary vane type steering machine. It is a horizontal sectional view of the pressure valve provided in the segment of the rotary vane type steering machine. It is a figure which shows the hydraulic circuit of a rotary vane type steering machine. It is a longitudinal cross-sectional view of the impact valve block of a rotary vane type steering machine.

Explanation of symbols

1 Housing 1b Segment 1m Back of vertical seal 2 Rotor 2d Vane 2e Upper horizontal slit 2f Upper horizontal seal 2g Lower horizontal slit 2h Lower horizontal seal 2i Vertical slit 2j Vertical seal 3 Top cover 5a, 5b, 5c, 5d Hydraulic oil chamber 8c, 8d Shock valve 9b Direction switching valve 9f Oil tank 9g Control hydraulic pump 9h Pressure adjustment valve 9i Control hydraulic line 9j Standard hydraulic line 10 Shock valve blocks 10a, 10b Outflow / inflow holes 10c, 10d Branch oil passages 10g, 10h Check valves 10i communication oil passage 10j block side oil supply passage 11a upper ring groove 11b sealing oil hole 12a cover side oil supply passage 13a pilot oil inlet 13b pilot oil check valve 13c pilot oil passage 13d pilot oil communication oil passage 14 vane 14a vane body 14b seal Suppressor 15a Top side 15 b Lower horizontal seal 15 c Vertical seal 15 d Upper end surface 15 e of the vertical seal Bottom surface of the upper horizontal seal on the radially outer end side (rear surface)
15f Lower end surface 15g of the vertical seal Upper surface (rear surface) on the radially outer end side of the lower horizontal seal
15h Vertical seal base 15i Vertical seal skirt 15k Upper horizontal seal recess 15m, 15n, 15o Upper horizontal seal bank 15p Upper horizontal seal base 15k 'Lower horizontal seal recess 15m', 15n ', 15o 'Lower horizontal seal base 15p' Lower horizontal seal bases 16a and 17a Upper left and right horizontal slits 16b and 17b Lower left and right horizontal slits 16c and 17c Left and right vertical slits 16d and 17d Upper left and right horizontal seals 16h and 17h Lower left and right horizontal seals 16l, 17l Left and right vertical seals 16m and 17m Left and right vertical seal bases 16n and 17n Left and right vertical seal first lips 16o and 17o Left and right vertical seal second lips 16q and 17q Upper left and right horizontal seal bottoms (back)
16r, 17r Lower left and right side seal upper surface (back)
16s, 17s Recesses 16t, 17t of the upper left and right lateral seals Recesses 16u, 17u of the lower left and right lateral seals Levees 16v, 17v of the upper left and right lateral seals 16m, 17w of the lower left and right lateral seals 16x, 17w 17x Lower left and right lateral seal base 18 Vane 18a Vane body 18c Vane bent portion 18e Housing bent portion 18f Curved slit 18g Curved seal 18j Curved seal base 18k Curved seal skirt portion 18n Seal restrainer 19a Seal 19b Base 19c Skirt 19d Slit 19e Sealing surface 19f Opposite sliding contact surface 19g Oil groove 19h Fine oil hole 19i Sealing oil hole D1 Clearance D2 Gap L1 Straight line S1 Bottom surface S2, S3 Side surface of vertical slit

Claims (5)

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 its front edge in the radial direction and both 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. The vertical slit is formed in the vertical slit, the vertical seal that is in sliding contact with the inner peripheral surface of the housing is inserted into the vertical slit, the upper horizontal seal that is in sliding contact with the back surface of the top cover is inserted in the upper horizontal slit, and the lower horizontal slit is inserted. The lower horizontal seal that is in sliding contact with the inner bottom surface of the housing is inserted, each of the seals is formed of an elastic material, the back surface of the vertical seal is connected to the back surfaces of the upper and lower horizontal seals, and the contact surface pressure is applied to the sliding surface. Pressure oil on the back of the vertical seal
One inflow / outflow hole communicating with the hydraulic oil chamber of the first group, the other outflow / inflow hole communicating with the hydraulic oil chamber of the second group, and the pressure oil flowing in from the one outflow / inflow hole into the other outflow / inflow hole Rotary vane rudder in which an anti-vibration valve block having one anti-vibration valve flowing out to the other and another anti-vibration valve flowing pressure oil flowing in from the other outflow / inflow hole to the one outflow / inflow hole is arranged A seal structure in a take-up machine,
An inlet of one check valve is connected to one branch oil passage branched from the one 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 communicating with the outlets of both check valves is provided in the anti-shock valve block, and the oil supply is made to communicate the communication oil passage of the anti-shock valve block with the annular upper ring groove provided on the upper end surface of the rotor. Rotary vane type characterized in that a passage is provided between the anti-vibration valve block and the top cover, and a sealing oil hole is provided through the vane from the rotor to communicate with the upper ring groove and the bottom surface of the vertical slit of the vane. Seal structure in the steering machine. A directional switching valve for switching the hydraulic oil supply destination to either the first group of hydraulic oil chambers or the second group of hydraulic oil chambers in a hydraulic circuit that supplies hydraulic oil to the hydraulic oil chamber, and switching of the directional switching valve And a control hydraulic pump that supplies control hydraulic pressure to control the direction switching valve from the control hydraulic line, and a pilot oil inlet, a pilot oil check valve, a pilot oil inlet, and a pilot oil A pilot oil passage that communicates with the inlet side of the check valve and a pilot oil communication oil passage that communicates with the outlet side of the pilot oil check valve and the communication oil passage are provided. 2. The seal structure for a rotary vane type steering machine according to claim 1, wherein an inlet communicates with the control hydraulic line. A directional control valve for switching a supply destination of the hydraulic oil discharged from the hydraulic pump to either the first group of hydraulic oil chambers or the second group of hydraulic oil chambers, to a hydraulic circuit that supplies the hydraulic oil to the hydraulic oil chamber; A return oil line from the direction switching valve to the oil tank, a pressure adjusting valve is provided in the return oil line, and the control hydraulic pressure for controlling the switching of the direction switching valve is directed from the discharge port side of the hydraulic pump. The line between the directional control valve and the pressure regulating valve is formed as a specified hydraulic line that is defined as a certain hydraulic pressure or more, and a pilot oil inlet and a , Pilot oil check valve, pilot oil passage communicating with pilot oil inlet and pilot oil check valve inlet side, pilot oil communicating oil communicating with pilot oil check valve outlet side and communication oil passage Road The seal structure in a rotary vane type steering machine according to claim 1, wherein a pilot oil inlet of the anti-shock valve block communicates with the specified hydraulic line or a discharge side line of the hydraulic pump. . 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. A seal structure in a rotary vane type steering machine partitioned into a plurality of hydraulic oil chambers,
A curved portion that is curved in an arc shape is formed in the lower corner portion of the tip surface of the vane, and an arc-shaped bent portion that is opposed to the curved portion of the vane is formed in the lower corner portion of the inner peripheral surface of the housing, An upper horizontal slit is formed in the upper end surface of the vane, and an upper horizontal seal that is slidably contacted with the back surface of the top cover is inserted into the upper horizontal slit. The radial direction of the lower end of the rotor passes through the bent portion from the tip surface of the vane. A curved slit that reaches the end surface is formed in the vane, and a curved seal that is in sliding contact with the inner peripheral surface and the inner bottom surface of the housing is inserted into the curved slit, and each of the seals is formed of an elastic material,
The curved seal protrudes from the both sides of the back surface formed on the opposite side of the base, the sealing surface that is in sliding contact with the inner peripheral surface and the inner bottom surface of the housing, and toward the back side of the curved slit. A pair of skirt portions opposed to each other in the direction, and the distal end portion of the skirt portion slightly protrudes outward in the circumferential direction from the side surface of the base portion in a free state before mounting.
The curved slit is composed of a bottom surface and a pair of side surfaces facing each other in the circumferential direction of the rotor, and the vane is divided into a vane body and a seal restrainer that can be attached to and detached from the vane body. The bottom surface and one side surface of the slit are formed, the other side surface of the curved slit is formed to suppress the seal, and the other side of the curved slit is opened in a state where the seal suppressor is removed from the vane body. Seal structure for rotary vane type steering machines. An oil groove is formed in the center in the circumferential direction of the seal surface of the seal, and communicates with the space between the bottom of the oil groove and the skirt on the back side or the recess on the bottom and back side of the oil groove. 5. The seal structure in a rotary vane type steering machine according to claim 4, wherein the fine oil hole to be formed is formed in a base portion of the seal.

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