An intermittent forward and reverse barring gear device driven by a hydraulic cylinder

Abstract

An intermittent forward and reverse turning gear driven by a hydraulic cylinder, which relates to a turning gear. The present invention aims to solve the problems that existing turning gears cannot provide a relatively accurate turning angle in some occasions, are sensitive to axial thermal expansion, and can only perform one-way automatic turning. The present invention includes a reverse turning gear ring, a forward turning gear ring, a forward turning oil cylinder I, a reverse turning oil cylinder I, a forward turning oil cylinder II, a reverse turning oil cylinder II, a forward turning electromagnetic reversing valve, and a reverse turning electromagnetic reversing valve. The forward turning gear ring and the reverse turning gear ring are coaxially fixed on the rotor shaft. On the outer side of the forward turning gear ring, the forward turning oil cylinder I and the forward turning oil cylinder II are arranged along the radial direction. The forward turning oil cylinder I and the forward turning oil cylinder II are respectively connected to the forward turning electromagnetic reversing valve. On the outer side of the reverse turning gear ring, the reverse turning oil cylinder I and the reverse turning oil cylinder II are arranged along the radial direction. The present invention is used for turning.

Description

Technical Field

[0001] The present invention relates to a barring gear device, in particular to an intermittent forward and reverse barring gear device driven by a hydraulic cylinder. Background Art

[0002] During the installation and inspection of units with large resistance torque and large moment of inertia, the rotor needs to be rotated by a fixed angle. For the convenience of installation, sometimes forward and reverse intermittent rotation is required. Traditional barring gear devices generally use motors to drive gear reduction devices to achieve continuous operation of barring. After the barring motor stops, the rotor continues to rotate due to inertia, and the angle through which the rotor rotates cannot be accurately controlled, which is not conducive to installation and maintenance. For the sake of compact structure, the axial clearance between the pinion for barring and the large gear for barring on the rotor of traditional barring gear devices is about 10 mm. In some cases, when the axial thermal expansion of the rotor exceeds the design value, axial collision occurs between the pinion for barring and the large gear for barring, resulting in interference damage to the barring gears and posing a great potential safety hazard. Existing barring gear devices generally use trapezoidal threads, spiral splines, and jaw couplings with inclined surfaces as torque transmission parts for barring clutches, which can achieve automatic disengagement of barring when the rotor speeds up. However, the problem is that only one-way barring can be achieved, and the clutch will automatically disengage during reverse barring, and two-way barring cannot be achieved. Summary of the Invention

[0003] In order to solve the problems that the existing barring gear device cannot provide a relatively accurate barring angle in some occasions, is sensitive to axial thermal expansion, and can only perform one-way automatic barring, the present invention further provides an intermittent forward and reverse barring gear device driven by a hydraulic cylinder.

[0004] The technical solution adopted by the present invention to solve the above technical problems is as follows:

[0005] An intermittent forward and reverse barring gear device driven by a hydraulic cylinder includes a reverse barring gear ring, a forward barring gear ring, a forward barring oil cylinder I, a reverse barring oil cylinder I, a forward barring oil cylinder II, a reverse barring oil cylinder II, a forward barring electromagnetic directional control valve, and a reverse barring electromagnetic directional control valve. The forward barring gear ring and the reverse barring gear ring are coaxially and fixedly connected to the rotor shaft. On the outer circumferential side wall of the forward barring gear ring, forward barring teeth are provided along the circumferential direction. On the outer circumferential side wall of the reverse barring gear ring, reverse barring teeth are provided along the circumferential direction. The inclination directions of the tooth working surfaces of the forward barring teeth and the reverse barring teeth are opposite. On the outer side of the forward barring gear ring, the forward barring oil cylinder I and the forward barring oil cylinder II are provided along the radial direction. The forward barring oil cylinder I and the forward barring oil cylinder II are respectively connected to the forward barring electromagnetic directional control valve. On the outer side of the reverse barring gear ring, the reverse barring oil cylinder I and the reverse barring oil cylinder II are provided along the radial direction. The reverse barring oil cylinder I and the reverse barring oil cylinder II are respectively connected to the reverse barring electromagnetic directional control valve.

[0006] The beneficial effects included in the present invention compared with the prior art are:

[0007] The present invention provides an automatic barring gear driven by a hydraulic cylinder and capable of intermittent forward and reverse rotation. In the present invention, there are two forward barring cylinders and two reverse barring cylinders respectively. The piston rods of the barring cylinders directly push the barring teeth on the barring gear ring, thereby driving the rotor shaft to rotate. The two cylinders for forward barring and the two barring cylinders for reverse are each controlled by an electromagnetic reversing valve. Each reversing valve realizes the intermittent alternating operation of the piston rods of the two cylinders by changing the oil circuit direction. The extension length of the piston rod can control the rotation angle of the rotor shaft, thereby realizing more precise control of the barring angle. When barring is not required, the piston rod retracts, and there is no interference between the rotor shaft and the barring gear ring. Two sets of barring gear rings, one for forward and one for reverse, are installed on the rotor. Each set of barring gear rings is alternately pushed by two cylinders to realize intermittent pushing of the barring gear ring to rotate, providing a barring device for the installation and maintenance of large units that can more precisely control the rotation angle and can perform barring in both forward and reverse directions. Brief Description of the Drawings

[0008] Figure 1 is a cross-sectional view of the overall structure of the present invention;

[0009] Figure 2 is a schematic diagram of the connection relationship after translating the end faces of the reverse barring gear ring 18 and the reverse barring teeth 26. At this time, the barring device is in the disengaged state, and the piston rod I 70 of the forward barring cylinder, the piston rod II 90 of the forward barring cylinder, the piston rod I 80 of the reverse barring cylinder, and the piston rod II 100 of the reverse barring cylinder are all retracted;

[0010] Figure 3 is a schematic diagram of the connection relationship after translating the end faces of the reverse barring gear ring 18 and the reverse barring teeth 26. At this time, the piston rod I 70 of the forward barring cylinder extends, the piston rod II 90 of the forward barring cylinder retracts, and the piston rod I 80 of the reverse barring cylinder and the piston rod II 100 of the reverse barring cylinder are retracted;

[0011] Figure 4 is a schematic diagram of the connection relationship after translating the end faces of the reverse barring gear ring 18 and the reverse barring teeth 26. At this time, the piston rod I 70 of the forward barring cylinder retracts, the piston rod II 90 of the forward barring cylinder extends, and the piston rod I 80 of the reverse barring cylinder and the piston rod II 100 of the reverse barring cylinder are retracted;

[0012] Figure 5 is a schematic diagram of the connection relationship after translating the end faces of the reverse barring gear ring 18 and the reverse barring teeth 26. At this time, the piston rod I 70 of the forward barring cylinder and the piston rod II 90 of the forward barring cylinder retract, the piston rod I 80 of the reverse barring cylinder extends, and the piston rod II 100 of the reverse barring cylinder retracts;

[0013] Figure 6This is a schematic diagram of the connection relationship after translating the end faces of the reverse turning gear ring 18 and the reverse turning gear 26 in the present invention. At this time, the piston rod I 70 of the forward turning oil cylinder and the piston rod II 90 of the forward turning oil cylinder are retracted, the piston rod I 80 of the reverse turning oil cylinder is retracted, and the piston rod II 100 of the reverse turning oil cylinder extends. Specific Embodiments

[0014] Specific Embodiment 1: In combination with Figures 1 to 4 This specific embodiment will be described. The intermittent forward and reverse turning device driven by a hydraulic cylinder described in this specific embodiment includes a reverse turning gear ring 18, a forward turning gear ring 28, a forward turning oil cylinder I 30, a reverse turning oil cylinder I 40, a forward turning oil cylinder II 50, a reverse turning oil cylinder II 60, a forward turning electromagnetic directional control valve 56, and a reverse turning electromagnetic directional control valve 66. The forward turning gear ring 28 and the reverse turning gear ring 18 are coaxially and fixedly connected to the rotor shaft 20. On the outer circumferential side wall of the forward turning gear ring 28, forward turning teeth 24 are provided along the circumferential direction. On the outer circumferential side wall of the reverse turning gear ring 18, reverse turning teeth 26 are provided along the circumferential direction. The inclined directions of the tooth working surfaces of the forward turning teeth 24 and the reverse turning teeth 26 are opposite. On the outer side of the forward turning gear ring 28, the forward turning oil cylinder I 30 and the forward turning oil cylinder II 50 are provided along the radial direction. The forward turning oil cylinder I 30 and the forward turning oil cylinder II 50 are respectively connected to the forward turning electromagnetic directional control valve 56. On the outer side of the reverse turning gear ring 18, the reverse turning oil cylinder I 40 and the reverse turning oil cylinder II 60 are provided along the radial direction. The reverse turning oil cylinder I 40 and the reverse turning oil cylinder II 60 are respectively connected to the reverse turning electromagnetic directional control valve 66.

[0015] With such a design, when the piston rods of the forward turning oil cylinder I 30 and the forward turning oil cylinder II 50 alternately extend and push the forward turning teeth 24, the rotor shaft 20 rotates intermittently in the forward direction. When the piston rods of the reverse turning oil cylinder I 40 and the reverse turning oil cylinder II 60 alternately extend and push the reverse turning teeth 26, the rotor shaft 20 rotates intermittently in the reverse direction. When the piston rods of the forward turning oil cylinder I 30, the reverse turning oil cylinder I 40, the forward turning oil cylinder II 50, and the reverse turning oil cylinder II 60 are retracted, the rotor shaft 20 can rotate freely and the axial thermal expansion is not interfered by the turning.

[0016] Specific Embodiment 2: In combination with Figures 1 to 2 This specific embodiment will be described. The forward turning gear ring 28 and the reverse turning gear ring 18 in this specific embodiment are respectively fixedly connected to the rotor shaft 20 through a plurality of connecting bolts. Other compositions and connection methods are the same as those in Specific Embodiment 1.

[0017] Specific Embodiment 3: In combination with Figures 1 to 2Referring to this embodiment, when the forward turning gear oil cylinder piston rod I70 of the forward turning gear oil cylinder I30 and the forward turning gear oil cylinder piston rod II90 of the forward turning gear oil cylinder II50 extend, they respectively act on the tooth working surfaces of the teeth of the forward turning gear 24. When the reverse turning gear oil cylinder piston rod I80 of the reverse turning gear oil cylinder I40 and the reverse turning gear oil cylinder piston rod II100 of the reverse turning gear oil cylinder II60 extend, they respectively act on the tooth working surfaces of the teeth of the reverse turning gear 26. Other components and connection methods are the same as those in the second specific embodiment.

[0018] Specific embodiment four: Figures 1 to 3 Referring to this embodiment, the intermittent forward and reverse turning gear device driven by a hydraulic cylinder according to this embodiment further includes a main electromagnetic directional control valve 79, and the main electromagnetic directional control valve 79 is respectively connected to the forward turning gear electromagnetic directional control valve 56 and the reverse turning gear electromagnetic directional control valve 66. Other components and connection methods are the same as those in the first, second, or third specific embodiment.

[0019] Specific embodiment five: Figures 1 to 3 Referring to this embodiment, the main electromagnetic directional control valve 79 is a three-position four-way solenoid valve. The left side of the main electromagnetic directional control valve 79 is provided with a main left electromagnet 74, and the right side of the main electromagnetic directional control valve 79 is provided with a main right electromagnet 76. The center position function is Y function. The P port of the main electromagnetic directional control valve 79 is connected to the pressure oil, and the O port of the main electromagnetic directional control valve 79 is connected to the oil tank. When neither the main left electromagnet 74 nor the main right electromagnet 76 is energized, the A port and the B port of the main electromagnetic directional control valve 79 are respectively communicated with the O port. When the main left electromagnet 74 is energized, the A port of the main electromagnetic directional control valve 79 is communicated with the P port and the B port is communicated with the O port. When the main right electromagnet 76 is energized, the B port of the main electromagnetic directional control valve 79 is communicated with the P port and the A port is communicated with the O port. Other components and connection methods are the same as those in the fourth specific embodiment.

[0020] Specific embodiment six: Figures 1 to 2 Referring to this embodiment, the forward turning gear electromagnetic directional control valve 56 is a two-position four-way solenoid valve. The left side of the forward turning gear electromagnetic directional control valve 56 is provided with a positive left electromagnet 54, and the right side of the forward turning gear electromagnetic directional control valve 56 is provided with a positive right electromagnet 58. The A port of the forward turning gear electromagnetic directional control valve 56 is connected to the rodless cavity of the forward turning gear oil cylinder I30 and the rod cavity of the forward turning gear oil cylinder II50 through an oil pipeline. The B port of the forward turning gear electromagnetic directional control valve 56 is connected to the rod cavity of the forward turning gear oil cylinder I30 and the rodless cavity of the forward turning gear oil cylinder II50 through an oil pipeline. When the positive left electromagnet 54 is energized, the A port of the forward turning gear electromagnetic directional control valve 56 is communicated with the P port and the B port is communicated with the O port. When the positive right electromagnet 58 is energized, the B port of the forward turning gear electromagnetic directional control valve 56 is communicated with the P port, the A port is communicated with the O port, the O port is connected to the oil tank, and the P port is connected to the A port of the main electromagnetic directional control valve 79. Other components and connection methods are the same as those in the fifth specific embodiment.

[0021] Embodiment VII: Combining Figures 1 to 2 and Figure 4 to describe this embodiment, in this embodiment, port A of the forward turning electromagnetic directional valve 56 is connected to the rodless cavity of the forward turning cylinder I 30 through the first forward oil pipe 32, port A of the forward turning electromagnetic directional valve 56 is connected to the rod cavity of the forward turning cylinder II 50 through the second forward oil pipe 36, port B of the forward turning electromagnetic directional valve 56 is connected to the rod cavity of the forward turning cylinder I 30 through the third forward oil pipe 34, and port B of the forward turning electromagnetic directional valve 56 is connected to the rodless cavity of the forward turning cylinder II 50 through the fourth forward oil pipe 38. Other components and connection methods are the same as those in Embodiment VI.

[0022] Embodiment VIII: Combining Figures 1 to 2 to describe this embodiment, in this embodiment, the reverse turning electromagnetic directional valve 66 is a two-position four-way solenoid valve. The left side of the reverse turning electromagnetic directional valve 66 is provided with a reverse left electromagnet 64, and the right side of the reverse turning electromagnetic directional valve 66 is provided with a reverse right electromagnet 68. Port A of the reverse turning electromagnetic directional valve 66 is connected to the rod cavity of the reverse turning cylinder I 40 and the rodless cavity of the reverse turning cylinder II 60 through an oil pipeline. Port B of the reverse turning electromagnetic directional valve 66 is connected to the rodless cavity of the reverse turning cylinder I 40 and the rod cavity of the reverse turning cylinder II 60 through an oil pipeline. When the reverse left electromagnet 64 is energized, port A of the reverse turning electromagnetic directional valve 66 is communicated with port P, and port B is communicated with port O. When the reverse right electromagnet 68 is energized, port B of the reverse turning electromagnetic directional valve 66 is communicated with port P, port A is communicated with port O, port O is connected to the fuel tank, and port P is connected to port B of the total electromagnetic directional valve 79. Other components and connection methods are the same as those in Embodiment VII.

[0023] Embodiment IX: Combining Figures 1 to 2 to describe this embodiment, in this embodiment, port A of the reverse turning electromagnetic directional valve 66 is connected to the rod cavity of the reverse turning cylinder I 40 through the first reverse oil pipe 44, port A of the reverse turning electromagnetic directional valve 66 is connected to the rodless cavity of the reverse turning cylinder II 60 through the second reverse oil pipe 48, port B of the reverse turning electromagnetic directional valve 66 is connected to the rodless cavity of the reverse turning cylinder I 40 through the third reverse oil pipe 42, and port B of the reverse turning electromagnetic directional valve 66 is connected to the rod cavity of the reverse turning cylinder II 60 through the fourth reverse oil pipe 46. Other components and connection methods are the same as those in Embodiment VIII.

[0024] Embodiment X: Combining Figures 1 to 3In this embodiment, a manual reversing switch 72 is provided on the total left electromagnet 74, a manual reversing switch 78 is provided on the total right electromagnet 76, a manual reversing switch 52 is provided on the positive left electromagnet 54, a manual reversing switch 59 is provided on the positive right electromagnet 58, a manual reversing switch 62 is provided on the reverse left electromagnet 64, and a manual reversing switch 69 is provided on the reverse right electromagnet 68. The other components and connection methods are the same as those in the eighth or ninth specific embodiments.

[0025] Figure 2 In this case, the total electromagnetic reversing valve 79 is de-energized, and there is no pressure oil in all oil circuits. The piston rod I 70 of the positive turning cylinder, the piston rod II 90 of the positive turning cylinder, the piston rod I 80 of the reverse turning cylinder, and the piston rod II 100 of the reverse turning cylinder are all in the retracted state. Since the piston rod I 70 of the positive turning cylinder, the piston rod II 90 of the positive turning cylinder, the piston rod I 80 of the reverse turning cylinder, and the piston rod II 100 of the reverse turning cylinder are all in the radial direction of the rotor shaft 20, the axial thermal expansion of the rotor shaft 20 will not interfere with the reverse turning gear ring 18 and the positive turning gear ring 28, reducing potential safety hazards. At this time, the rotor can be in a stationary state or a high-speed rotating state, and the rotor can rotate freely without being interfered by turning during axial thermal expansion.

[0026] Figure 3 In this case, the total electromagnetic reversing valve 79 operates, the total left electromagnet 74 is energized, the total right electromagnet 76 is de-energized, the positive left electromagnet 54 is energized, and the positive right electromagnet 58 is de-energized. The pressure oil enters the rodless cavity of the positive turning cylinder I 30 from the main oil pipe 94 through the total first oil pipe 96 and the positive first oil pipe 32, pushing the piston rod I 70 of the positive turning cylinder to extend and driving the positive turning gear 24 to rotate. At the same time, the pressure oil enters the rod cavity of the positive turning cylinder II 50 from the main oil pipe 94 through the total first oil pipe 96 and the positive second oil pipe 36, pushing the piston rod II 90 of the positive turning cylinder to retract. The positive turning gear 24 rotates only under the action of the piston rod I 70 of the positive turning cylinder, and the rotor shaft 20 rotates forward. The rotation angle is determined by the extension distance of the piston rod and the outer diameter of the turning gear. At this time, the total right electromagnet 76 is de-energized, and there is no pressure oil passing through the reverse turning cylinder I 40 and the reverse turning cylinder II 60. The piston rod I 80 of the reverse turning cylinder and the piston rod II 100 of the reverse turning cylinder are both in the retracted state, and the reverse turning gear 24 will not interfere with the operation of the positive turning.

[0027] Figure 4Among them, the total electromagnetic reversing valve 79 operates, the total left electromagnet 74 is energized, the total right electromagnet 76 is de-energized, the positive left electromagnet 54 is de-energized, and the positive right electromagnet 58 is energized. The pressure oil enters the rodless cavity of the positive turning cylinder II 50 from the main oil pipe 94 through the total first oil pipe 96 and the positive fourth oil pipe 38, pushing the piston rod II 90 of the positive turning cylinder to extend, and driving the positive turning gear 24 to rotate. At the same time, the pressure oil enters the rod cavity of the positive turning cylinder I 30 from the main oil pipe 94 through the total first oil pipe 96 and the positive third oil pipe 34, pushing the piston rod I 70 of the positive turning cylinder to retract. The positive turning gear 24 rotates only under the action of the piston rod II 90 of the positive turning cylinder, and the rotor shaft 20 rotates positively. The rotation angle is determined by the extension distance of the piston rod and the outer diameter of the turning gear. At this time, the total right electromagnet 76 is de-energized, and no pressure oil passes through the reverse turning cylinder I 40 and the reverse turning cylinder II 60. The piston rod I 80 of the reverse turning cylinder and the piston rod II 100 of the reverse turning cylinder are both in the retracted state, and the reverse turning gear 24 will not interfere with the operation of the positive turning.

[0028] Figure 5 Among them, the total electromagnetic reversing valve 79 operates, the total left electromagnet 74 is de-energized, the total right electromagnet 76 is energized, the reverse left electromagnet 64 is de-energized, and the reverse right electromagnet 68 is energized. The pressure oil enters the rodless cavity of the reverse turning cylinder I 40 from the main oil pipe 94 through the total second oil pipe 92 and the reverse third oil pipe 42, pushing the piston rod I 80 of the reverse turning cylinder to extend, and driving the reverse turning gear 26 to rotate. At the same time, the pressure oil enters the rod cavity of the reverse turning cylinder II 60 from the main oil pipe 94 through the total second oil pipe 92 and the reverse fourth oil pipe 46, pushing the piston rod II 100 of the reverse turning cylinder to retract. The reverse turning gear 26 rotates only under the action of the piston rod I 80 of the reverse turning cylinder, and the rotor shaft 20 rotates reversely. The rotation angle is determined by the extension distance of the piston rod and the outer diameter of the turning gear. At this time, the total left electromagnet 74 is de-energized, and no pressure oil passes through the positive turning cylinder I 30 and the positive turning cylinder II 50. The piston rod I 70 of the positive turning cylinder and the piston rod II 90 of the positive turning cylinder are both in the retracted state, and the positive turning gear 24 will not interfere with the operation of the reverse turning.

[0029] Figure 6Among them, the total electromagnetic reversing valve 79 operates, the total left electromagnet 74 is de-energized, the total right electromagnet 76 is energized, the reverse left electromagnet 64 is energized, and the reverse right electromagnet 68 is de-energized. The pressure oil enters the rodless cavity of the reverse turning cylinder II 60 from the main oil pipe 94 through the main second oil pipe 92 and the reverse second oil pipe 48, pushing the piston rod II 100 of the reverse turning cylinder to extend and driving the reverse turning gear 26 to rotate. At the same time, the pressure oil enters the rod cavity of the reverse turning cylinder I 40 from the main oil pipe 94 through the main second oil pipe 92 and the reverse first oil pipe 44, pushing the piston rod I 80 of the reverse turning cylinder to retract. The reverse turning gear 26 only rotates under the action of the piston rod II 100 of the reverse turning cylinder, and the rotor shaft 20 rotates in the reverse direction. The rotation angle is determined by the extension distance of the piston rod and the outer diameter of the turning gear. At this time, the total left electromagnet 74 is de-energized, and there is no pressure oil passing through the forward turning cylinder I 30 and the forward turning cylinder II 50. The piston rod I 70 of the forward turning cylinder and the piston rod II 90 of the forward turning cylinder are both in the retracted state, and the forward turning gear 24 will not interfere with the operation of the reverse turning.

[0030] Although the present invention has been described herein with reference to specific embodiments, it should be understood that these embodiments are merely examples of the principles and applications of the present invention. Therefore, it should be understood that many modifications can be made to the exemplary embodiments, and other arrangements can be designed, as long as they do not depart from the spirit and scope of the present invention as defined by the appended claims. It should be understood that the different dependent claims and the features described herein can be combined in a manner different from that described in the original claims. It should also be understood that the features described in connection with a single embodiment can be used in other described embodiments.

Claims

1. An intermittent forward and reverse barring gear driven by a hydraulic cylinder, characterized in that: The described intermittent forward and reverse barring gear device driven by a hydraulic cylinder includes a reverse barring gear ring (18), a forward barring gear ring (28), a forward barring oil cylinder I (30), a reverse barring oil cylinder I (40), a forward barring oil cylinder II (50), a reverse barring oil cylinder II (60), a forward barring electromagnetic directional control valve (56), and a reverse barring electromagnetic directional control valve (66). The forward barring gear ring (28) and the reverse barring gear ring (18) are coaxially and fixedly connected to the rotor shaft (20). Along the circumferential direction on the outer circumferential side wall of the forward barring gear ring (28), forward barring teeth (24) are provided. Along the circumferential direction on the outer circumferential side wall of the reverse barring gear ring (18), reverse barring teeth (26) are provided. The inclination directions of the tooth working surfaces of the forward barring teeth (24) and the reverse barring teeth (26) are opposite. On the outer side of the forward barring gear ring (28), along the radial direction, a forward barring oil cylinder I (30) and a forward barring oil cylinder II (50) are provided. The forward barring oil cylinder I (30) and the forward barring oil cylinder II (50) are respectively connected to the forward barring electromagnetic directional control valve (56). On the outer side of the reverse barring gear ring (18), along the radial direction, a reverse barring oil cylinder I (40) and a reverse barring oil cylinder II (60) are provided. The reverse barring oil cylinder I (40) and the reverse barring oil cylinder II (60) are respectively connected to the reverse barring electromagnetic directional control valve (66). When the piston rods of the forward barring oil cylinder I (30) and the forward barring oil cylinder II (50) alternately extend and push the forward barring teeth (24), the rotor shaft (20) rotates intermittently in the forward direction. When the piston rods of the reverse barring oil cylinder I (40) and the reverse barring oil cylinder II (60) alternately extend and push the reverse barring teeth (26), the rotor shaft (20) rotates intermittently in the reverse direction. When the piston rods of the forward barring oil cylinder I (30), the reverse barring oil cylinder I (40), the forward barring oil cylinder II (50), and the reverse barring oil cylinder II (60) retract, the rotor shaft (20) can rotate freely, and the axial thermal expansion is not interfered by the barring gear.

2. The intermittent forward and reverse barring gear driven by a hydraulic cylinder according to claim 1, characterized in that: The forward barring gear ring (28) and the reverse barring gear ring (18) are respectively fixedly connected to the rotor shaft (20) through a plurality of connecting bolts.

3. The intermittent positive and reverse barring gear driven by a hydraulic cylinder according to claim 2, characterized in that: When the forward barring oil cylinder piston rod I (70) of the forward barring oil cylinder I (30) and the forward barring oil cylinder piston rod II (90) of the forward barring oil cylinder II (50) extend, they respectively act on the tooth working surfaces of the forward barring teeth (24). When the reverse barring oil cylinder piston rod I (80) of the reverse barring oil cylinder I (40) and the reverse barring oil cylinder piston rod II (100) of the reverse barring oil cylinder II (60) extend, they respectively act on the tooth working surfaces of the reverse barring teeth (26).

4. The intermittent forward and reverse barring gear driven by a hydraulic cylinder according to claim 1, 2 or 3, characterized in that: The described intermittent forward and reverse barring gear device driven by a hydraulic cylinder further includes a master electromagnetic directional control valve (79). The master electromagnetic directional control valve (79) is respectively connected to the forward barring electromagnetic directional control valve (56) and the reverse barring electromagnetic directional control valve (66).

5. The intermittent forward and reverse barring gear driven by a hydraulic cylinder according to claim 4, characterized in that: The total electromagnetic directional control valve (79) is a three-position four-way solenoid valve. The left side of the total electromagnetic directional control valve (79) is equipped with a total left electromagnet (74), and the right side of the total electromagnetic directional control valve (79) is equipped with a total right electromagnet (76). The neutral position function is of Y type. The P port of the total electromagnetic directional control valve (79) is connected to the pressure oil, and the O port of the total electromagnetic directional control valve (79) is connected to the oil tank. When neither the total left electromagnet (74) nor the total right electromagnet (76) is energized, the A port and B port of the total electromagnetic directional control valve (79) are respectively connected to the O port. When the total left electromagnet (74) is energized, the A port of the total electromagnetic directional control valve (79) is connected to the P port and the B port is connected to the O port. When the total right electromagnet (76) is energized, the B port of the total electromagnetic directional control valve (79) is connected to the P port and the A port is connected to the O port.

6. The intermittent forward and reverse barring gear driven by a hydraulic cylinder according to claim 5, characterized in that: The forward barring electromagnetic directional control valve (56) is a two-position four-way solenoid valve. The left side of the forward barring electromagnetic directional control valve (56) is equipped with a positive left electromagnet (54), and the right side of the forward barring electromagnetic directional control valve (56) is equipped with a positive right electromagnet (58). The A port of the forward barring electromagnetic directional control valve (56) is connected to the rodless cavity of the forward barring oil cylinder I (30) and the rod cavity of the forward barring oil cylinder II (50) through an oil pipeline. The B port of the forward barring electromagnetic directional control valve (56) is connected to the rod cavity of the forward barring oil cylinder I (30) and the rodless cavity of the forward barring oil cylinder II (50) through an oil pipeline. When the positive left electromagnet (54) is energized, the A port of the forward barring electromagnetic directional control valve (56) is connected to the P port and the B port is connected to the O port. When the positive right electromagnet (58) is energized, the B port of the forward barring electromagnetic directional control valve (56) is connected to the P port, the A port is connected to the O port, the O port is connected to the oil tank, and the P port is connected to the A port of the total electromagnetic directional control valve (79).

7. An intermittent forward and reverse barring gear driven by a hydraulic cylinder according to claim 6, wherein: The A port of the forward barring electromagnetic directional control valve (56) is connected to the rodless cavity of the forward barring oil cylinder I (30) through a forward first oil pipe (32), and the A port of the forward barring electromagnetic directional control valve (56) is connected to the rod cavity of the forward barring oil cylinder II (50) through a forward second oil pipe (36). The B port of the forward barring electromagnetic directional control valve (56) is connected to the rod cavity of the forward barring oil cylinder I (30) through a forward third oil pipe (34), and the B port of the forward barring electromagnetic directional control valve (56) is connected to the rodless cavity of the forward barring oil cylinder II (50) through a forward fourth oil pipe (38).

8. The intermittent forward and reverse barring gear driven by a hydraulic cylinder according to claim 7, wherein: The reverse barring electromagnetic directional control valve (66) is a two-position four-way solenoid valve. The left side of the reverse barring electromagnetic directional control valve (66) is equipped with a reverse left electromagnet (64), and the right side of the reverse barring electromagnetic directional control valve (66) is equipped with a reverse right electromagnet (68). The port A of the reverse barring electromagnetic directional control valve (66) is connected to the rod chamber of the reverse barring oil cylinder I (40) and the rodless chamber of the reverse barring oil cylinder II (60) through an oil pipeline. The port B of the reverse barring electromagnetic directional control valve (66) is connected to the rodless chamber of the reverse barring oil cylinder I (40) and the rod chamber of the reverse barring oil cylinder II (60) through an oil pipeline. When the reverse left electromagnet (64) is energized, the port A of the reverse barring electromagnetic directional control valve (66) is communicated with the port P, and the port B is communicated with the port O. When the reverse right electromagnet (68) is energized, the port B of the reverse barring electromagnetic directional control valve (66) is communicated with the port P, the port A is communicated with the port O, the port O is connected to the fuel tank, and the port P is connected to the port B of the main electromagnetic directional control valve (79).

9. The intermittent forward and reverse barring gear driven by a hydraulic cylinder according to claim 7, wherein: The port A of the reverse barring electromagnetic directional control valve (66) is connected to the rod chamber of the reverse barring oil cylinder I (40) through a reverse first oil pipe (44), and the port A of the reverse barring electromagnetic directional control valve (66) is connected to the rodless chamber of the reverse barring oil cylinder II (60) through a reverse second oil pipe (48). The port B of the reverse barring electromagnetic directional control valve (66) is connected to the rodless chamber of the reverse barring oil cylinder I (40) through a reverse third oil pipe (42), and the port B of the reverse barring electromagnetic directional control valve (66) is connected to the rod chamber of the reverse barring oil cylinder II (60) through a reverse fourth oil pipe (46).

10. The intermittent forward and reverse barring gear driven by a hydraulic cylinder according to claim 8 or 9, characterized in that: A main left manual reversing switch (72) is provided on the main left electromagnet (74), a main right manual reversing switch (78) is provided on the main right electromagnet (76), a positive left manual reversing switch (52) is provided on the positive left electromagnet (54), a positive right manual reversing switch (59) is provided on the positive right electromagnet (58), a reverse left manual reversing switch (62) is provided on the reverse left electromagnet (64), and a reverse right manual reversing switch (69) is provided on the reverse right electromagnet (68).

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