O-groove sealing mechanism for split flange face of runner chamber

Abstract

The invention discloses a runner chamber halving flange face O-groove sealing mechanism, and relates to the technical field of flange sealing, the runner chamber halving flange face O-groove sealing mechanism comprises a runner chamber, one end of the runner chamber is connected with a second cavity through a connecting assembly, the connecting assembly is provided with a sealing mechanism and an adjusting mechanism, and the sealing mechanism has a common sealing working state and a reinforced sealing working state; the adjusting mechanism is used for driving and adjusting the sealing mechanism to be switched between a common sealing state and a reinforced sealing state; the sealing mechanism has a common sealing working mode and a reinforced sealing working mode, when the rotating wheel in the rotating wheel chamber works at a low speed, the sealing mechanism seals the rotating wheel in a common sealing mode to prevent water leakage, the vibration amplitude of the rotating wheel chamber is also enhanced along with the increase of the rotating speed of the rotating wheel in the rotating wheel chamber, and at the moment, the rotating wheel is sealed. The adjusting mechanism drives sealing to be switched from a common sealing state to a reinforced sealing state, and the situation that due to increase of the vibration amplitude, water leakage of equipment is aggravated is prevented.

Description

Technical Field

[0001] The invention relates to the field of flange sealing, and in particular to an O-groove sealing mechanism for a half-flange surface of a runner chamber. Background Art

[0002] The runner chamber is a key part of the operation of the turbine. It is usually the area used to accommodate the turbine rotor (runner). It is mainly used to guide the water flow into the turbine and is responsible for converting the kinetic energy of the water flow into mechanical energy, thereby driving the generator to generate electricity. In existing turbine installations, flanges are usually used to fix the runner chamber to the turbine to ensure the stability and safety of the structure.

[0003] For example, the invention authorization patent with publication number CN110374781B and publication date October 16, 2020 discloses a sealing structure of a water turbine expansion joint, including a tailwater pipe flange and a runner chamber tail flange, an expansion joint is arranged between the tailwater pipe flange and the runner chamber tail flange, the expansion joint includes an expansion joint pressure plate and an expansion joint flange, the expansion joint flange is fixedly connected to the tailwater pipe flange, the expansion joint pressure plate and the expansion joint flange are fixedly connected, the inner circle of the expansion joint is provided with a sealing ring that seals with the side of the runner chamber tail flange, a sealing strip is arranged between the end face of the tailwater pipe flange and the end face of the runner chamber tail flange, and the inner circle of the tailwater pipe flange is provided with a sealing strip pressure plate that radially acts on the sealing strip; this patent provides a water turbine expansion joint sealing structure whose sealing effect is not affected by the vibration of the runner chamber and effectively prevents water leakage from the expansion joint.

[0004] When the existing impeller chamber is connected to the turbine, it is usually connected through a half-flange. When the existing half-flange is assembled, glue is usually applied to the surface of the half-flange for auxiliary sealing. However, since the impeller chamber is made of an inner layer of stainless steel and an outer layer of carbon steel inlaid by a combination process, the expansion coefficients of the two materials are different, resulting in different deformation amounts due to thermal expansion and contraction. In addition, the vibration generated during the operation of the rotating shaft in the impeller chamber can easily lead to water leakage at the connection of the half-flange. As the rotation speed of the rotating shaft increases, the vibration in the impeller chamber will become greater and greater, and the increasing degree of vibration will also aggravate the leakage and affect the normal operation of the turbine. Summary of the invention

[0005] The object of the present invention is to provide a half-flange surface O-groove sealing mechanism for a runner chamber to solve the above-mentioned deficiencies in the prior art.

[0006] In order to achieve the above object, the present invention provides the following technical solutions:

[0007] A runner chamber half-flange surface O-groove sealing mechanism comprises a runner chamber, one end of which is connected to a second chamber via a connecting assembly, a sealing mechanism and an adjusting mechanism are arranged on the connecting assembly, and the sealing mechanism has two working states: ordinary sealing and enhanced sealing;

[0008] The adjusting mechanism is used to drive the sealing mechanism to switch between a normal sealing state and an enhanced sealing state.

[0009] The above-mentioned connecting assembly includes a first half flange, a second half flange and connecting bolts, the first half flange is connected to the impeller chamber, the second half flange is connected to the second chamber, and the connecting bolts connect the first half flange and the second half flange, wherein a avoidance groove is provided on the surface of the first half flange close to the second half flange, and the sealing mechanism is arranged in the avoidance groove.

[0010] As mentioned above, both the first half flange and the second half flange are provided with avoidance grooves, and the avoidance grooves on the first half flange and the second half flange are staggered.

[0011] As mentioned above, the sealing mechanism includes a rubber sealing ring, a load-bearing ring and a plurality of adjusting springs. The rubber sealing ring is placed in a avoidance groove. The end of the rubber sealing ring located in the avoidance groove is connected to the load-bearing ring. The load-bearing ring and the avoidance groove are connected by a plurality of adjusting springs. The plurality of adjusting springs are arranged at circumferential intervals along the load-bearing ring.

[0012] The above-mentioned adjustment mechanism includes a plurality of adjustment grooves provided on the first half flange, the plurality of adjustment grooves all connect the inner cavity of the runner chamber with the avoidance groove, and the plurality of adjustment grooves are arranged at intervals along the circumference of the first half flange.

[0013] As mentioned above, a transmission rod is rotatably installed in the adjusting groove, the axial direction of the transmission rod is parallel to the width direction, a bevel gear is installed at one end of the transmission rod located in the inner cavity of the wheel chamber through a torsion spring, the bevel gear is coaxial with the transmission rod, a transmission groove is opened on the surface of the transmission rod, a matching sleeve is provided on the outer side of the transmission rod, an insert block is installed on the inner circumferential surface of the matching sleeve, and a plurality of push rods are also arranged in the avoidance groove, the plurality of push rods are arranged at intervals along the circumference of the avoidance groove, one end of the push rod abuts against the surface of the bearing ring, and the other end of the push rod abuts against the surface of the matching sleeve.

[0014] As mentioned above, the wheel chamber is provided with a wheel, a coaxial driving shaft is provided on the wheel, a connecting rod is fixedly installed on the driving shaft, a driving gear block is fixedly installed on one end of the connecting rod away from the driving shaft, and the driving gear block is provided with helical teeth matching with the bevel gear.

[0015] As mentioned above, the transmission groove includes a rectangular spiral groove and an annular groove, and the annular groove is located on the side of the transmission rod away from the bevel gear.

[0016] As mentioned above, the matching sleeve is divided into an inclined surface section and a plane section along the width direction, and the inclined surface section is farther away from the bevel gear than the plane section.

[0017] As mentioned above, the cross section of the avoidance groove is large in belly and small in mouth, and the width of the avoidance groove increases gradually from the groove mouth to the groove bottom.

[0018] The beneficial effect of the present invention is that in the above technical scheme, the sealing mechanism provided by the present invention has two working modes: ordinary sealing and enhanced sealing. When the impeller in the impeller chamber is working at a low speed, the sealing mechanism seals it in an ordinary sealing manner to prevent water leakage. As the speed of the impeller in the impeller chamber increases, the vibration amplitude of the impeller chamber also increases. At this time, the adjustment mechanism drives the seal to switch from the ordinary sealing state to the enhanced sealing state based on the change in the vibration level in the impeller chamber, so as to prevent the equipment from leaking more due to the increase in vibration amplitude. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in the present invention. For ordinary technicians in this field, other drawings can also be obtained based on these drawings.

[0020] Figure 1 A schematic diagram of the structure of the sealing mechanism provided in an embodiment of the present invention connecting the runner chamber and the second chamber;

[0021] Figure 2 A schematic diagram of the internal structure of the runner chamber and the second chamber provided in an embodiment of the present invention;

[0022] Figure 3 The embodiment of the present invention provides Figure 2 A magnified schematic diagram of point A;

[0023] Figure 4 A schematic diagram of the state of the push rod when the drive shaft according to an embodiment of the present invention rotates at high speed;

[0024] Figure 5 A schematic diagram of the structure of a transmission groove on a transmission rod provided in an embodiment of the present invention;

[0025] Figure 6 A schematic diagram of the structure of a matching sleeve provided in an embodiment of the present invention;

[0026] Figure 7 A schematic diagram of the connection between the matching sleeve and the transmission rod provided in an embodiment of the present invention;

[0027] Figure 8 A schematic diagram of the cooperation between the driving gear block and the bevel gear provided in an embodiment of the present invention;

[0028] Fig. 9 A schematic diagram of the cooperation between a torsion spring and a helical gear ring provided in another embodiment of the present invention;

[0029] Fig.10 A schematic top view of a helical gear ring provided in another embodiment of the present invention.

[0030] Description of reference numerals:

[0031] 1. Wheel chamber; 2. Connecting assembly; 21. First half flange; 22. Second half flange; 23. Avoidance groove; 3. Second chamber; 4. Sealing mechanism; 41. Rubber sealing ring; 42. Loading ring; 43. Adjusting spring; 5. Adjusting mechanism; 51. Adjusting groove; 52. Transmission rod; 53. Bevel gear; 54. Transmission groove; 541. Rectangular spiral groove; 542. Annular groove; 55. Matching sleeve; 551. Inclined section; 552. Plane section; 56. Insert block; 57. Push rod; 58. Connecting rod; 59. Driving gear block; 6. Torsion spring; 61. Bevel gear ring. DETAILED DESCRIPTION

[0032] In order to enable those skilled in the art to better understand the technical solution of the present invention, Figure 1-10 , the present invention is further introduced in detail.

[0033] In each embodiment of the present invention, for the convenience of description and understanding, the axial direction of the wheel is called the length direction, the direction perpendicular to the length direction on the horizontal plane is called the width direction, and the direction of gravity is called the vertical direction, that is, the length direction, the width direction and the vertical direction constitute a three-dimensional rectangular coordinate system.

[0034] The embodiment of the present invention provides a runner chamber half-flange surface O-groove sealing mechanism, comprising a runner chamber 1, one end of the runner chamber 1 is connected to a second chamber 3 via a connecting assembly 2, a sealing mechanism 4 and an adjusting mechanism 5 are arranged on the connecting assembly 2, and the sealing mechanism 4 has two working states: ordinary sealing and enhanced sealing;

[0035] The adjusting mechanism 5 is used to drive the sealing mechanism 4 to switch between the normal sealing state and the enhanced sealing state.

[0036] Specifically, a runner is usually arranged in the existing runner chamber 1. The runner is the core part of the turbine and is responsible for converting the kinetic energy of the water flow into rotational motion, thereby realizing the transmission of power. This is the existing technology and its principle will not be repeated here. The connecting component 2 can be connected by flange, thread, pipe joint, pipe glue and other connection methods. In the present embodiment, the connecting component 2 is preferably connected to the second chamber 3 by flange connection, wherein the second chamber 3 refers to other components connected to the runner chamber 1, such as: material inlet, material outlet, transmission chamber (chamber or pipeline for transmitting liquid), etc., wherein, in the present embodiment, the second chamber 3 can be selected as a transmission chamber. When the runner is rotating, the liquid moves in the runner chamber 1 and the second chamber 3, wherein the connecting component 2 is used as a connecting piece to connect the runner chamber 1 and the second chamber 3 to prevent the liquid from flowing out from the connection between the runner chamber 1 and the second chamber 3, and ensure the air tightness of the liquid when flowing in the runner chamber 1 and the second chamber 3.

[0037] However, when the existing flange-type connecting assembly 2 seals two cavities (in this embodiment, the wheel chamber 1 and the second chamber 3), in order to improve the sealing effect during the flange connection, glue is usually applied to the surface of the flange to increase the stability of the seal. However, since the wheel chamber 1 is made of an inner layer of stainless steel and an outer layer of carbon steel inlaid in a combined process, the expansion coefficients of the two materials are different, resulting in different deformation amounts due to thermal expansion and contraction. In addition, the wheel in the wheel chamber 1 will vibrate during operation, which can easily cause water leakage at the flange connection. The ordinary glue coating method cannot effectively prevent the leakage from occurring. Moreover, as the wheel speed increases, the vibration of the wheel chamber 1 will become greater and greater, and the increasing degree of vibration will also aggravate the leakage and affect the normal operation of the equipment.

[0038] In order to solve the above problems, in the present embodiment, a sealing mechanism 4 is provided on the connection component 2, and the sealing mechanism 4 has two working states: ordinary sealing and enhanced sealing. The sealing mechanism 4 can use a rubber sealing ring, which is annular and coaxially arranged with the flange. Moreover, a placement groove for placing the sealing ring is opened on one of the flanges, and the sealing ring is installed in the placement groove. The other end of the sealing ring protrudes from the flange surface (when the two flanges are connected together by bolts, the sealing ring is compressed). When the sealing mechanism 4 is in the ordinary sealing state, the sealing ring installed on the flange is only actively squeezed by the other flange because it protrudes from the surface of one flange; when the sealing mechanism 4 is in the enhanced sealing state, the sealing ring is not only subjected to the extrusion force provided by the other flange, but also subjected to the active compression force opposite to the direction of the force (that is, the extrusion force provided by the other flange), that is, the two flanges Both provide active extrusion pressure (here active extrusion force refers to the relative movement between the contact part on the flange and the sealing ring to increase the sealing performance). The compression force acts on the sealing ring, so that the sealing ring is tightly attached to the surface of the other flange to enhance the airtightness of the sealing mechanism 4; in this embodiment, the adjustment mechanism 5 can use a combination of a linear drive and a sensor, the linear drive is connected to the sealing ring, and the sensor is used to monitor the rotation speed of the impeller. When the rotation speed of the impeller reaches the monitoring threshold of the sensor, the sensor sends an electrical signal to the linear drive, and the linear drive drives the sealing ring to move toward the direction of the other flange, so that the sealing ring is tightly pressed against the surface of the other flange, thereby improving the sealing of the flange by increasing the tightness between the sealing ring and the flange, thereby avoiding the impeller in the impeller chamber 1 from rotating rapidly, resulting in an increase in the vibration amplitude of the flange, causing water leakage at the connection of the flange.

[0039] Obviously, if the sealing ring is in a compressed state from the beginning, the connection position will maintain a highly sealed state at this time. Even if the high rotation speed of the impeller causes the impeller chamber 1 to be in a low vibration state or a high vibration state, the equipment can maintain a highly sealed state and the liquid in the impeller chamber 1 can be prevented from leaking out of the connection position. However, when the impeller is in a low rotation speed, the vibration amplitude of the impeller chamber 1 is small, and the sealing ring does not need to be in a compressed manner for sealing (the ordinary manner can be used for sealing, resulting in unnecessary waste). If the sealing ring is in a compressed state for a long time, that is, the sealing ring is subjected to continuous pressure for a long time, it is easy to cause the shape of the sealing ring to change, and even cause its surface to be damaged or deformed, and may accelerate the aging and wear of the sealing ring. , causing the sealing ring to lose its original elasticity and shorten its life. After a period of time, the sealing ring will not be sealed tightly and cannot effectively prevent liquid leakage. In addition, due to the shortened life of the sealing ring, frequent maintenance and replacement are required, which is not worth the loss. In this embodiment, the sealing mechanism 4 has two working modes: ordinary sealing and enhanced sealing. When the rotor is at a low speed, the sealing mechanism 4 is in an ordinary sealing state; when the rotor is at a high speed, the sealing mechanism 4 is in an enhanced sealing state. Compared with the sealing ring being in a compressed state for a long time, in this embodiment, the sealing ring adjusts the degree of sealing according to different working environments. On the premise of ensuring the sealing of the equipment, it can also effectively extend the service life of the sealing ring.

[0040] Among them, when using an electric-controlled telescopic rod to pressurize the sealing ring, the pressure on the sealing ring is not uniform. When the sealing ring is under pressure, it is easy for the local pressure to be too high. At this time, the area where the pressure of the sealing ring is too high is prone to excessive wear. If the pressure on the sealing ring is uneven, the sealing performance of the sealing ring will not necessarily increase, and there is uncertainty in improving the sealing effect.

[0041] In this embodiment, preferably, the connecting assembly 2 includes a first half flange 21, a second half flange 22 and connecting bolts, the first half flange 21 is connected to the impeller chamber 1, the second half flange 22 is connected to the second chamber 3, and the connecting bolts connect the first half flange 21 with the second half flange 22, wherein a avoidance groove 23 is provided on the surface of the first half flange 21 close to the second half flange 22, and a sealing mechanism 4 is arranged in the avoidance groove 23, wherein the sealing mechanism 4 includes a rubber sealing ring 41, a load ring 42 and a plurality of adjustment springs 43, the rubber sealing ring 41 is placed in the avoidance groove 23, and the rubber sealing ring 41 is located in the avoidance groove A load-bearing ring 42 is connected to the end of the position groove 23, and the load-bearing ring 42 is used to evenly apply pressure to the rubber sealing ring 41. The load-bearing ring 42 is connected to the bottom wall of the position-avoiding groove 23 by a plurality of adjusting springs 43, and the plurality of adjusting springs 43 are arranged at intervals along the circumference of the load-bearing ring 42, wherein the adjusting mechanism 5 includes a plurality of adjusting grooves 51 opened on the first half-flange 21, and the plurality of adjusting grooves 51 all connect the inner cavity of the runner chamber 1 with the position-avoiding groove 23, and the plurality of adjusting grooves 51 are arranged at intervals along the circumference of the first half-flange 21, and a transmission rod 52 is rotatably installed in the adjustment groove 51 by a torsion spring 6, and the axial direction of the transmission rod 52 is perpendicular to the position of the position-avoiding groove 23. In the length direction (that is, the axial direction of the transmission rod 52 is perpendicular to the axial direction of the runner), a bevel gear 53 is installed at one end of the transmission rod 52 located in the inner cavity of the runner chamber 1, and the bevel gear 53 is coaxial with the transmission rod 52. A transmission groove 54 is opened on the surface of the transmission rod 52. The transmission groove 54 includes a rectangular spiral groove 541 and an annular groove 542. The annular groove 542 is located on the side of the transmission rod 52 away from the bevel gear 53. A matching sleeve 55 is sleeved on the outer side of the transmission rod 52, and an insert block 56 is installed on the inner circumferential surface of the matching sleeve 55. In the initial state, one end of the insert block 56 is inserted into the rectangular spiral groove 541; wherein, the matching sleeve 55 is radially divided along the runner chamber 1. It is a bevel section 551 and a plane section 552. The bevel section 551 is farther away from the bevel gear 53 than the plane section 552, and a plurality of push rods 57 are arranged in the avoidance groove 23. The plurality of push rods 57 are arranged at intervals along the circumference of the avoidance groove 23. One end of the push rod 57 abuts against the surface of the bearing ring 42, and the other end of the push rod 57 abuts against the bevel section 551 of the matching sleeve 55. In addition, a coaxial driving shaft is arranged on the rotating wheel, and a connecting rod 58 is fixedly installed on the driving shaft. An arc-shaped driving tooth block 59 is fixedly installed on the end of the connecting rod 58 away from the driving shaft, and the driving tooth block 59 is provided with helical teeth matching with the bevel gear 53.

[0042] Specifically, in the present embodiment, the avoidance groove 23 is annular, and the rubber sealing ring 41 is placed in the avoidance groove 23. In the initial state (that is, when the adjusting spring 43 is not subjected to force), one end of the rubber sealing ring 41 protrudes from the avoidance groove 23. When the first half-flange 21 is connected to the second half-flange 22, the first half-flange 21 and the second half-flange 22 are locked together under the action of the connecting bolts. At this time, under the extrusion of the second half-flange 22, the adjusting spring 43 connecting the load-bearing ring 42 and the rubber sealing ring 41 is compressed. However, under the action of the elastic force, the adjusting spring 43 has a tendency to reset, so that the adjusting spring 43 pushes the load-bearing ring 42 with the adjusting spring 43 toward the second half-flange 22. The rubber sealing ring 41 is moved to the right side so that the rubber sealing ring 41 is tightly pressed against the surface of the second half flange 22; wherein, the bearing ring 42, as a transition part, can evenly spread the elastic force provided by the adjusting spring 43 to the rubber sealing ring 41, so that the rubber sealing ring 41 is evenly pressed on the second half flange 22, and the situation of uneven sealing caused by local excessive pressing can be avoided; and, the rectangular spiral groove 541 is connected with the annular groove 542, and the interface between the rectangular spiral groove 541 and the annular groove 542 is arc-shaped, so that the plug 56 can enter from the annular groove 542 into the rectangular spiral groove 541; wherein, when the runner is working in the runner chamber 1, the sealing mechanism 4 mainly has the following two working states:

[0043] The first is: when the wheel is in the low-speed working mode, as the wheel rotates at a low speed, the wheel rotates synchronously with the driving shaft, connecting rod 58 and driving gear block 59. As the driving gear block 59 rotates, the driving gear block 59 intermittently passes the position of the bevel gear 53. Because the driving gear block 59 has helical teeth that match the bevel gear 53, when the driving gear block 59 passes through the bevel gear 53, the helical teeth on the driving gear block 59 mesh with the bevel gear 53, and the bevel gear 53 rotates synchronously with the transmission rod 52. At this time, the torsion spring 6 connected to the transmission rod 52 accumulates elastic potential energy, but the helical teeth on the driving gear block 59 only exist partially, and the rotation speed of the wheel is relatively low. After the driving gear block 59 leaves the bevel gear 53, the torsion spring 6 releases the accumulated elastic potential energy, and the torsion spring 6 drives the transmission rod 52 and the bevel gear 53 to reset. Moreover, before the torsion spring 6 drives the bevel gear 53 to reset, due to the low rotation speed of the wheel, the driving gear block 59 cannot continue to mesh with the bevel gear 53. The bevel gear 53 is meshed, so that the bevel gear 53 will continuously repeat the intermittent rotation and resetting action, which cannot affect the rubber sealing ring 41 of the sealing mechanism 4. At this time, the sealing mechanism 4 always maintains a normal sealing state, which is the state of the rubber sealing ring 41 when the first half flange 21 and the second half flange 22 are connected by connecting bolts. When the first half flange 21 and the second half flange 22 are connected by connecting bolts, the first half flange 21 and the second half flange 22 are connected together. At this time, under the extrusion of the second half flange 22, the adjusting spring 43 connecting the load-bearing ring 42 and the rubber sealing ring 41 is compressed. Under the elastic force of the adjusting spring 43, the adjusting spring 43 has a tendency to reset. At this time, the adjusting spring 43 pushes the load-bearing ring 42 to move with the adjusting spring 43 in the direction of the second half flange 22, so that the rubber sealing ring 41 is against the surface of the second half flange 22 to seal the connection.

[0044] The second is: when the wheel is in high-speed working mode, as the wheel rotates at high speed, the wheel drives the driving shaft, the connecting rod 58 and the driving gear block 59 to rotate synchronously. As the driving gear block 59 rotates, the driving gear block 59 passes the position of the bevel gear 53. Because there are helical teeth on the driving gear block 59 that match the bevel gear 53, when the driving gear block 59 passes the bevel gear 53, the helical teeth on the driving gear block 59 mesh with the bevel gear 53, and the bevel gear 53 drives the transmission rod 52 to rotate synchronously. At this time, the torsion spring 6 connected to the transmission rod 52 accumulates elastic potential energy, and, Because the wheel rotates at a high speed, before the torsion spring 6 releases the accumulated elastic potential energy to reset the transmission rod 52 and the bevel gear 53, the driving tooth block 59 passes the position of the bevel gear 53 again, so that the bevel gear 53 continues to accumulate elastic potential energy. As the wheel continues to rotate at a high speed, the bevel gear 53 continues to rotate with the transmission rod 52. At this time, the transmission rod 52 rotates around its own axis. As the transmission rod 52 rotates, the rectangular spiral groove 541 on the transmission rod 52 drives the insert block 56 to slide along the width direction in the direction away from the bevel gear 53 until the insert block 56 The insert block 56 moves from the rectangular spiral groove 541 to the annular groove 542. During the movement, the insert block 56 moves synchronously with the matching sleeve 55. As the matching sleeve 55 moves, the end of the push rod 57 slides along the inclined section 551 of the matching sleeve 55. Under the action of the inclined section 551, the push rod 57 also continuously slides along the length direction, driving the other end of the push rod 57 to continuously squeeze the load ring 42, driving the load ring 42 to move toward the direction of the rubber sealing ring 41, compressing the rubber sealing ring 41. When the insert block 56 moves into the annular groove 542, the insert block 56 moves synchronously with the matching sleeve 55. As the matching sleeve 55 moves, the end of the push rod 57 slides along the inclined section 551 of the matching sleeve 55. Under the action of the inclined section 551, the push rod 57 also continuously slides along the length direction, driving the other end of the push rod 57 to continuously squeeze the load ring 42, driving the load ring 42 to move toward the direction of the rubber sealing ring 41, compressing the rubber sealing ring 41. , the push rod 57 also moves to the plane section 552 of the matching sleeve 55. At this time, the push rod 57 moves to the extreme position. At this time, the pressure on the rubber sealing ring 41 is the greatest. The rubber sealing ring 41 is subjected to a strong pressure toward the second half-flange 22. The rubber sealing ring 41 under pressure contacts with the second half-flange 22, which can improve the sealing performance of the connection between the first half-flange 21 and the second half-flange 22, and avoid leakage at the connection position between the first half-flange 21 and the second half-flange 22 due to vibration when the wheel rotates at high speed.

[0045] Obviously, when the water flow speed in the turbine decreases, the runner switches from the high-speed working mode to the low-speed working mode, and the reset process is as follows: when the runner switches from the high-speed working mode to the low-speed working mode, the runner rotates at a low speed, and the runner under low-speed rotation brings the drive shaft, the connecting rod 58 and the drive gear block 59 to intermittently mesh with the bevel gear 53. When the drive gear block 59 is separated from the bevel gear 53, the torsion spring 6 releases the accumulated elastic potential energy, and the torsion spring 6 drives the transmission rod 52 to rotate in the opposite direction. Under the action of gravity, the insert block 56 enters from the annular groove 542 into the rectangular spiral groove 541, and as it rotates As the transmission rod 52 continues to rotate, the insert block 56 slides along the width direction toward the direction close to the bevel gear 53. During the movement of the insert block 56, the insert block 56 synchronously moves with the matching sleeve 55 toward the direction close to the bevel gear 53. As the matching sleeve 55 moves, the end of the push rod 57 contacts the inclined surface section 551 of the matching sleeve 55 again, and the other end of the push rod 57 moves with the load-bearing ring 42 toward the direction away from the rubber sealing ring 41. The rubber sealing ring 41 returns to the normal sealing state to seal the connection between the first half-flange 21 and the second half-flange 22.

[0046] The key point of this embodiment lies in the selection of the torsion spring 6 on the transmission rod 52, wherein the water flow velocity entering the water wheel chamber can be adjusted by the guide vanes in the water wheel chamber, and the water flow rate can be controlled by adjusting the angle of the guide vanes, thereby adjusting the water flow velocity in the water wheel chamber. This is a prior art and its principle will not be repeated. Since the water flow velocity entering the water wheel chamber is adjustable, it is obvious that the rotation speed of the impeller is also known, so the rotation speed of the connecting rod 58 and the driving tooth block 59 driven by it is also known. If the resistance of the selected torsion spring 6 is too small, the connecting rod 58 and the driving tooth block 59 can continuously drive the transmission rod 52 to rotate. If the resistance of the selected torsion spring 6 is too large, the connecting rod 58 and the driving tooth block 59 may never be able to continuously drive the transmission rod 52 to rotate. Obviously, those skilled in the art can select a suitable type of torsion spring 6 through limited experiments to obtain that the drive shaft cannot continuously drive the transmission rod 52 to rotate through the connecting rod 58 and the driving tooth block 59 under low speed state, and the drive shaft can continuously drive the transmission rod 52 to rotate through the connecting rod 58 and the driving tooth block 59 under high speed state.

[0047] Obviously, the avoidance groove 23 does not have to be opened on the first half flange 21, but can also be opened on the second half flange 22, or even on both the first half flange 21 and the second half flange 22. In this case, it is only necessary to stagger the avoidance grooves 23 on the first half flange 21 and the second half flange 22. Moreover, when the avoidance grooves 23 are opened on both the first half flange 21 and the second half flange 22, and sealing mechanisms 4 are arranged in the avoidance grooves 23, the connection position will have a better sealing effect through the joint action of multiple sealing mechanisms 4.

[0048] Furthermore, in the present embodiment, since the adjusting groove 51 connects the annular groove 542 with the inner cavity of the wheel chamber 1, when there is liquid inside the inner cavity of the wheel chamber 1, the liquid will gradually penetrate into the annular groove 542 along the adjusting groove 51. At this time, if the cross-section of the annular groove 542 is rectangular, the restriction of the rubber sealing ring 41 alone may not necessarily prevent the liquid from seeping out of the annular groove 542.

[0049] In this regard, preferably, the cross-section of the avoidance groove 23 is large in belly and small in mouth, and the width of the avoidance groove 23 gradually increases from the groove opening to the groove bottom, wherein the cross-section of the avoidance groove 23 is preferably an isosceles trapezoid, and the cross-sectional size of the rubber sealing ring 41 is larger than the groove opening size of the avoidance groove 23, that is, as the rubber sealing ring 41 leaves the avoidance groove 23 under the action of external force (the elastic force of the adjustment spring 43 or the thrust of the push rod 57), the rubber sealing ring 41 will inevitably deform under the extrusion of the avoidance groove 23, and the deformed rubber sealing ring 41 is tightly attached to the groove wall of the avoidance groove 23 under the action of elasticity. The avoidance groove 23 is blocked to prevent water from seeping out of the avoidance groove 23, and when the liquid enters the annular groove 542 through the adjusting groove 51, the increasing liquid in the adjusting groove 51 will also give the rubber sealing ring 41 a thrust (liquid pressure) toward the second half-flange 22. At this time, the pressure on the rubber sealing ring 41 is further increased, further improving the sealing between the first half-flange 21 and the second half-flange 22, thereby preventing the liquid in the runner chamber 1 from flowing out from the connection between the first half-flange 21 and the second half-flange 22.

[0050] Obviously, in this embodiment, after long-term use, the rubber sealing ring 41 located in the avoidance groove 23 is squeezed and contacted with the second half-flange 22 for a long time. The side of the rubber sealing ring 41 in contact with the second half-flange 22 is prone to aging. The aged rubber will become brittle and its compressive strength will decrease. When the aged rubber is subjected to strong pressure, the aged rubber cannot withstand it and is prone to breakage or crushing. At this time, the thickness of the rubber sealing ring 41 will be reduced. When the rubber sealing ring 41 is subjected to the previous pressure (that is, in the above embodiment, the force applied by the push rod 57 to the load-bearing ring 42), the rubber The rubber sealing ring 41 cannot reach the compression state in the above-mentioned embodiment (in other words, the distance that the push rod 57 pushes the load-bearing ring 42 to move is the compression thickness of the rubber sealing ring 41, and now the push rod 57 pushes the load-bearing ring 42 to move the distance including the compression thickness of the rubber sealing ring 41 and the distance from the rubber sealing ring 41 to the surface of the second half-flange 22. Generally speaking, the compression thickness of the rubber sealing ring 41 is reduced, so the aged rubber sealing ring 41 cannot achieve the previous sealing effect when being compressed), which directly affects the sealing performance of the rubber sealing ring 41 at the connection between the first half-flange 21 and the second half-flange 22.

[0051] In order to solve the above problems, Figure 9-10 As shown, in another embodiment of the present invention, the torsion spring 6 is sleeved on the outside of the transmission rod 52, the torsion spring 6 is coaxial with the transmission rod 52, and the outside of the torsion spring 6 is sleeved with a bevel gear ring 61, which is fixedly installed in the adjustment groove 51, and the bevel gear ring 61 is coaxial with the transmission rod 52.

[0052] Specifically, in the present embodiment, the bevel gear ring 61 is annular, and the bevel teeth on the bevel gear ring 61 are arranged on its inner circumferential surface, wherein the two pins of the torsion spring 6 are arranged at intervals along the width direction, and the pin of the torsion spring 6 close to the bevel gear 53 is fixedly mounted on the side wall of the transmission rod 52, and the pin of the torsion spring 6 away from the bevel gear 53 is inserted into the tooth groove of the bevel gear ring 61, and the tooth groove is the notch between two adjacent tooth blocks on the bevel gear ring 61, wherein, when the surface of the rubber sealing ring 41 does not age, the rubber sealing ring 41 reaches a reinforced sealing state, and the pin of the torsion spring 6 will not be removed from the bevel gear. The tooth groove on the ring 61 is disengaged (at this time, the pin of the torsion spring 6 is already at the limit position on the tooth groove. If the torsion spring 6 continues to accumulate force, the pin of the torsion spring 6 will be easily disengaged from the tooth groove); when the surface of the rubber sealing ring 41 is aged, in order to achieve an enhanced sealing state, the rubber sealing ring 41 needs to move a larger distance, and then the transmission rod 52 needs to rotate more circles. At this time, the degree of force accumulation of the torsion spring 6 is greater than before (when the rubber sealing ring 41 has not aged), so that the pin of the torsion spring 6 will be disengaged from the initial tooth groove and enter the next tooth groove.

[0053] It should be noted that, for the convenience of description and understanding, when the rotating wheel drives the driving shaft and the transmission rod 52 to rotate, the transmission rod 52 rotates in the clockwise direction.

[0054] Furthermore, in this embodiment, when the rubber sealing ring 41 is aged, the sealing process of the rubber sealing ring 41 at the connection position between the first half flange 21 and the second half flange 22 is as follows:

[0055] First, with the high-speed rotation of the rotating wheel, the rotating wheel drives the driving shaft, the connecting rod 58 and the driving gear block 59 to rotate synchronously. With the rotation of the driving gear block 59, the driving gear block 59 passes the position of the bevel gear 53. Since the driving gear block 59 has helical teeth that match the bevel gear 53, when the driving gear block 59 passes through the bevel gear 53, the helical teeth on the driving gear block 59 mesh with the bevel gear 53, and the bevel gear 53 rotates the transmission rod 52 in the clockwise direction. Since one pin of the torsion spring 6 is fixedly mounted on the transmission rod 52, and the other pin is inserted into the tooth groove of the helical gear ring 61, as the transmission rod 52 rotates on its own, the transmission rod 52 rotates in the clockwise direction synchronously with the torsion spring 6. Since the rubber sealing ring 41 has aged, in order to achieve a strengthened sealing state, the rubber sealing ring 41 has a rubber The sealing ring 41 needs to move a longer distance under the action of the push rod 57, and the transmission rod 52 also needs to rotate more circles. At this time, the force storage degree of the torsion spring 6 is greater than before (when the rubber sealing ring 41 is not aged). At this time, the pin of the torsion spring 6 located in the tooth groove of the helical gear ring 61 moves upward along the helical teeth on the helical gear ring 61 until it is disengaged from the tooth groove. In addition, as the pin of the torsion spring 6 moves upward along the helical teeth on the helical gear ring 61, the torsion spring 6 is stretched along the width direction (that is, the axial direction of the transmission rod 52). At this time, the torsion spring 6 accumulates elastic potential energy. When the pin of the torsion spring 6 is disengaged from the tooth groove and enters above the next tooth groove (the tooth groove adjacent to the above tooth groove), there is no restricting object below the torsion spring 6, and the torsion spring 6 releases the accumulated elastic potential energy, and the pin of the torsion spring 6 enters the next tooth groove of the helical gear ring 61.

[0056] Subsequently, when the rubber sealing ring 41 is reset to restore to the normal sealing state, the pin of the torsion spring 6 located in the tooth groove of the helical gear ring 61 is separated from the original tooth groove and enters another tooth groove, that is, the position of the pin is changed, so that the two pins of the torsion spring 6 are relatively displaced. At this time, the torsion spring 6 accumulates elastic potential energy, but the pin is blocked by the helical teeth on the helical gear ring 61 and cannot be reset, and the other pin of the torsion spring 6 is fixedly connected to the transmission rod 52, so that the torsion spring 6 can only drive the transmission rod 52 to rotate in the clockwise direction to release the accumulated elastic potential energy of the torsion spring 6. Elastic potential energy, when the transmission rod 52 rotates in the clockwise direction, the rectangular spiral groove 541 on the transmission rod 52 drives the plug block 56 to slide along the width direction in the direction away from the bevel gear 53. During the movement of the plug block 56, the plug block 56 moves upward a certain distance with the matching sleeve 55. When the matching sleeve 55 moves upward, the matching sleeve 55 squeezes the push rod 57, so that the push rod 57 pushes the bearing ring 42 to move a certain distance toward the position of the rubber sealing ring 41. The moving distance is used to offset the thickness loss of the rubber sealing ring 41 due to aging.

[0057] The above description is only by way of illustration of certain exemplary embodiments of the present invention. It is undoubted that those skilled in the art can modify the described embodiments in various ways without departing from the spirit and scope of the present invention. Therefore, the above drawings and descriptions are illustrative in nature and should not be construed as limiting the scope of protection of the claims of the present invention.

Claims

1. A wheel chamber half-flange surface O-groove sealing mechanism, comprising a wheel chamber (1), one end of the wheel chamber (1) being connected to a second chamber (3) via a connecting assembly (2), characterized in that: The connection assembly (2) is provided with a sealing mechanism (4) and an adjusting mechanism (5), and the sealing mechanism (4) has two working states: ordinary sealing and enhanced sealing; The adjustment mechanism (5) is used to drive the sealing mechanism (4) to switch between a normal sealing state and a reinforced sealing state.

2. The O-groove sealing mechanism for the half-flange surface of the runner chamber according to claim 1, characterized in that: The connecting assembly (2) comprises a first half flange (21), a second half flange (22) and connecting bolts, wherein the first half flange (21) is connected to the runner chamber (1), and the second half flange (22) is connected to the second chamber (3), and the connecting bolts connect the first half flange (21) and the second half flange (22), wherein a relief groove (23) is provided on a surface of the first half flange (21) close to the second half flange (22), and a sealing mechanism (4) is arranged in the relief groove (23).

3. The O-groove sealing mechanism for the half-flange surface of the runner chamber according to claim 2, characterized in that: The first half flange (21) and the second half flange (22) are both provided with avoidance grooves (23), and the avoidance grooves (23) on the first half flange (21) and the second half flange (22) are staggered.

4. The O-groove sealing mechanism for the half-flange surface of the runner chamber according to claim 2, characterized in that: The sealing mechanism (4) comprises a rubber sealing ring (41), a bearing ring (42) and a plurality of adjusting springs (43); the rubber sealing ring (41) is placed in the avoidance groove (23); the end of the rubber sealing ring (41) located in the avoidance groove (23) is connected to the bearing ring (42); the bearing ring (42) and the avoidance groove (23) are connected via the plurality of adjusting springs (43); and the plurality of adjusting springs (43) are arranged at intervals along the circumference of the bearing ring (42).

5. The O-groove sealing mechanism for the half-flange surface of the runner chamber according to claim 4, characterized in that: The adjustment mechanism (5) comprises a plurality of adjustment grooves (51) formed on the first half flange (21), the plurality of adjustment grooves (51) all connecting the inner cavity of the runner chamber (1) with the avoidance groove (23), and the plurality of adjustment grooves (51) are arranged at intervals along the circumference of the first half flange (21).

6. The O-groove sealing mechanism for the half-flange surface of the runner chamber according to claim 5, characterized in that: A transmission rod (52) is rotatably mounted in the adjustment groove (51), the axial direction of the transmission rod (52) being parallel to the width direction, a bevel gear (53) is mounted on one end of the transmission rod (52) located in the inner cavity of the wheel chamber (1) through a torsion spring (6), the bevel gear (53) being coaxial with the transmission rod (52), a transmission groove (54) being provided on the surface of the transmission rod (52), a matching sleeve (55) being sleeved on the outer side of the transmission rod (52), an insert block (56) being mounted on the inner circumferential surface of the matching sleeve (55), and a plurality of push rods (57) being arranged in the avoidance groove (23), the plurality of push rods (57) being arranged at intervals along the circumference of the avoidance groove (23), one end of the push rod (57) being pressed against the surface of the bearing ring (42), and the other end of the push rod (57) being pressed against the surface of the matching sleeve (55).

7. The O-groove sealing mechanism for the half-flange surface of the runner chamber according to claim 6, characterized in that: The wheel chamber (1) is provided with a wheel, a coaxial driving shaft is provided on the wheel, a connecting rod (58) is fixedly mounted on the driving shaft, a driving tooth block (59) is fixedly mounted on one end of the connecting rod (58) away from the driving shaft, and the driving tooth block (59) is provided with helical teeth matching with the bevel gear (53).

8. The O-groove sealing mechanism for the half-flange surface of the runner chamber according to claim 7, characterized in that: The transmission groove (54) comprises a rectangular spiral groove (541) and an annular groove (542), and the annular groove (542) is located on a side of the transmission rod (52) away from the bevel gear (53).

9. The O-groove sealing mechanism for the half-flange surface of the runner chamber according to claim 8, characterized in that: The matching sleeve (55) is divided into an inclined surface section (551) and a plane section (552) along the width direction. The inclined surface section (551) is farther away from the bevel gear (53) than the plane section (552).

10. The O-groove sealing mechanism of the half-flange surface of the runner chamber according to claim 9, characterized in that: The cross section of the avoidance groove (23) is large in the belly and small in the mouth, and the width of the avoidance groove (23) gradually increases from the groove mouth to the groove bottom.

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