Cutting rock breaking mechanism and cutting method

Abstract

The invention relates to a cutting rock-breaking mechanism and a cutting method, and the cutting rock-breaking mechanism comprises a cutter assembly which comprises a sun gear rotating around a first axis; the planet gears are arranged at intervals in the circumferential direction, and eccentric structures are arranged on the planet gears; the planet wheel mandrel is sleeved with the planet wheel and rotationally connected with the planet wheel so as to bear inertia moment and / or radial inertia force which alternately rotates around the first axis; the planet carrier is coaxial with the first axis and is fixedly connected with the planet wheel mandrel; the cutterhead frame is connected with the planet carrier; when the planet carrier alternately rotates around the first axis, the cutter head frame reciprocates along the first axis and / or alternately rotates around the first axis; when the planet carrier swings in the radial direction, the cutterhead frame swings in the radial direction in a rotating mode. And the cutter is fixedly connected with the cutter head frame and has an eccentric distance. Rock is cut and broken under the multiple actions of extrusion feeding force of the cutter, vibration impact of the cutter and radial eccentric impact rock breaking, so that the rock breaking capacity (productivity) and the rock breaking efficiency are improved, the specific energy consumption of rock breaking is reduced, and the cutter is suitable for breaking hard rock.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of cutting, in particular to a cutting rock breaking mechanism and a cutting method. BACKGROUND

[0002] The cantilever partial section tunneling machine is the mainstream equipment in the coal roadway and semi-coal rock roadway tunneling construction. The working mechanism of the equipment is usually equipped with a cutting head provided with multiple cutting teeth. In operation, the cutting head is driven by the tunneling machine to wedge into the coal rock by extruding the coal rock and relying on the cutting force of the cutting teeth, so as to realize breaking and tunneling. However, from the actual cutting performance, the existing cutting head structure is difficult to effectively deal with hard rock roadway with a Protodyakonov hardness coefficient f>8. Due to the high hardness of such rock mass, the required working extrusion force is huge, which not only causes the significant rise of the energy consumption of the whole machine, but also causes the transmission of strong reaction force to the cutting head, resulting in the rapid acceleration of the wear of the cutting teeth and the significant shortening of the service life. In addition, the breaking is only relied on the extrusion force in a single direction, the breaking method is relatively single, and the breaking efficiency is low. The reaction force generated during the operation is further transmitted to the whole machine through the cutting head, which easily causes strong vibration, affecting the stability and working reliability of the equipment.

[0003] According to statistics, the total length of the roadway tunneling in China is about 9000 kilometers every year, of which the full rock roadway accounts for 20% to 30%, and about 90% of such roadway still relies on the traditional blasting tunneling method for construction. Therefore, developing a cantilever partial section tunneling machine working mechanism capable of efficiently cutting hard rock, having strong adaptability and high reliability has become a key technical problem to be solved in the current industry. SUMMARY

[0004] (I) Technical problem to be solved

[0005] In view of the above-mentioned shortcomings and deficiencies of the prior art, the present application provides a cutting rock breaking mechanism and a cutting method, which can efficiently cut hard rock, have strong adaptability and high reliability.

[0006] (II) Technical scheme

[0007] In order to achieve the above-mentioned purpose, the main technical scheme adopted by the present application comprises:

[0008] In a first aspect, the present application provides a cutting rock breaking mechanism, comprising a cutter assembly, which comprises:

[0009] A sun gear capable of rotating around a first axis;

[0010] A plurality of planet gears arranged circumferentially and spaced apart around the first axis and engaged with the sun gear, and an eccentric structure is arranged on the planet gears;

[0011] A planetary gear spindle is provided for the planetary gears to be fitted and rotatably connected, so as to bear the inertial torque and / or rotational radial inertial force transmitted by the multiple planetary gears rotating alternately about the first axis.

[0012] The planetary gear carrier is coaxial with the first axis and is fixedly connected to the planetary gear spindle;

[0013] The cutter head is movably connected to the planetary gear carrier; when the planetary gear carrier rotates alternately around the first axis, the cutter head reciprocates along the first axis and / or rotates alternately around the first axis; when the planetary gear carrier oscillates radially, the cutter head oscillates radially in a rotational manner.

[0014] The cutting tool is fixedly connected to the tool holder, and there is an eccentricity between its axis and the rotation center of the tool holder.

[0015] According to the present invention, the eccentric structures on the plurality of planetary gears are symmetrically arranged about the first axis, and the plurality of planetary gears are capable of transmitting an inertial torque that alternates around the first axis to the planetary gear spindle; or,

[0016] The eccentric structures on adjacent planetary gears are 180° out of phase, and the multiple planetary gears can transmit rotational radial inertial force to the planetary gear spindle; or,

[0017] The phase difference of the eccentric structures on adjacent planetary gears is 90°, and the multiple planetary gears can transmit alternating rotational inertial torque and rotational radial inertial force to the planetary gear spindle.

[0018] According to the present invention, a receiving cavity is formed inside the planetary gear, and the eccentric structure is a lead block or lead powder disposed inside the receiving cavity.

[0019] According to the present invention, a connecting shaft is provided at the front end of the planetary gear carrier;

[0020] The rear end of the cutter head holder is sleeved on the connecting shaft and connected to the connecting shaft through a lead screw and nut structure or an internal and external helical tooth structure;

[0021] The outer periphery of the planetary gear carrier is provided with a first limiting member and a second limiting member at intervals along the first axial direction, and the cutter head can move along the first axial direction to abut against the first limiting member or the second limiting member.

[0022] According to the present invention, the first limiting member is a thrust bearing sleeved on the journal at the front end of the connecting shaft;

[0023] The journal is provided with a first annular groove and a second annular groove at intervals from back to front along the first axial direction; a four-part retaining ring is inserted in the first annular groove, and the four-part retaining ring abuts against the end face of the first limiting member; an elastic retaining ring is inserted in the second annular groove, and a retaining sleeve is fitted on the journal between the four-part retaining ring and the elastic retaining ring, and the inner circumference of the retaining sleeve abuts against the outer circumference of the four-part retaining ring and the first limiting member;

[0024] The second limiting member is a thrust bearing sleeved on the outer periphery of the planetary gear carrier.

[0025] According to the present invention, it also includes a housing having the aforementioned cutting tool assembly disposed therein;

[0026] A sliding sleeve is provided between the outer periphery of the cutter head holder and the inner wall of the outer shell, and the sliding sleeve is used to support the axial movement and rotation of the cutter head holder.

[0027] According to the present invention, the front end of the cutter head holder extends beyond the front end of the housing, and a sealing assembly is fixedly disposed at the front end of the housing. The sealing assembly is located on the front side of the sliding sleeve, and the sealing assembly includes:

[0028] The sealing seat has a first sealing groove and a second sealing groove sequentially formed from front to back along the first axial direction on its inner circumference.

[0029] An axially floating sealing sleeve and a compressible expandable grease chamber are provided in the first sealing groove. The axially floating sealing sleeve and the cutter head are in clearance fit. The rear end of the axially floating sealing sleeve abuts against the compressible expandable grease chamber. The compressible expandable grease chamber contains and discharges hydraulic oil when pressurized.

[0030] And a skeleton oil seal disposed in the second sealing groove;

[0031] When the compressible expandable grease chamber is filled with grease, the axial floating seal sleeve can squeeze the compressible expandable grease chamber to discharge the grease.

[0032] According to the present invention, an axially extending oil passage is provided on the outer casing;

[0033] The oil inlet of the oil circuit is used to connect to the built-in hydraulic oil injector or the external grease gun, and the oil circuit is provided with multiple oil outlets;

[0034] The sliding sleeve is provided with a plurality of first oil inlet channels connecting the outer periphery of the sliding sleeve and the outer shell, and connecting the inner periphery of the sliding sleeve and the cutter head holder. The first oil inlet channels are connected to the oil outlet.

[0035] The cutter head holder has a second oil inlet channel with a damping hole. One end of the second oil inlet channel is connected to the first oil inlet channel, and the other end is connected to the connection part between the cutter head holder and the planetary gear carrier.

[0036] According to the present invention, the tool assembly further includes a rotation drive member, the drive end of which is connected to the sun gear for driving the sun gear to rotate.

[0037] Secondly, the present invention also provides a cutting method applied to the aforementioned cutting and rock-breaking mechanism, wherein the cutting method is as follows:

[0038] S1. The cutting tool of the rock-breaking mechanism is driven by the tunneling machine to wedge into the rock;

[0039] S2. The sun gear drives multiple planetary gears to rotate synchronously around the first axis and rotate on their own axis. The planetary gears transmit alternating inertial torque and / or radial inertial force to the planetary gear spindle and the planetary gear carrier, driving the cutter head holder and the cutter to reciprocate along the first axis, rotate alternatingly around the first axis, reciprocate axially combined with radial oscillation, or rotate alternatingly combined with radial oscillation, so that the cutter vibrates and impacts to crush rock. During the process of vibrating and impacting to crush rock, the cutter can also radially eccentrically impact and crush rock.

[0040] (III) Beneficial Effects

[0041] The beneficial effects of this invention are as follows: This rock-breaking cutting mechanism drives multiple planetary gears with eccentric structures to revolve and rotate via a sun gear. The planetary gears are mounted on a planetary gear carrier via planetary gear spindles. The resultant force of the inertial forces generated by the eccentric structures of the multiple planetary gears acts on the planetary gear spindle, forming alternating inertial torque, radial inertial force, or a composite force of alternating inertial torque and radial inertial force. Specifically, the alternating inertial torque can excite the planetary gear carrier to rotate alternatingly around a first axis, the radial inertial force can excite the planetary gear carrier to oscillate radially, and the composite force of alternating inertial torque and radial inertial force can excite the planetary gear carrier to perform a composite motion of alternating rotation and radial oscillation around the first axis. The planetary gear carrier can transmit dynamic load to the cutterhead holder connected to it: when the planetary gear carrier rotates alternatingly around the first axis, the cutterhead holder reciprocates along the first axis and / or rotates synchronously around the first axis; when the planetary gear carrier oscillates radially, the cutterhead holder oscillates synchronously radially. Furthermore, the tool holder can drive the tool to undergo axial reciprocating motion, circumferential alternating rotation, radial oscillation, a combination of axial reciprocating motion and radial oscillation, or a combination of circumferential alternating rotation and radial oscillation. Simultaneously, due to the eccentricity between the tool's axis and the tool holder's rotation center, the tool can also generate radial impact force during its movement.

[0042] Therefore, this rock-breaking mechanism enables the cutter to vibrate and impact the rock during the process of the tunneling machine driving the cutter to wedge into the rock. The cutter can rotate circumferentially, oscillate radially, reciprocate axially, or combine circumferential and axial movements, or combine radial and axial movements in multiple trajectories, and also impact the rock radially eccentrically. This multi-action approach, combining the squeezing force of the cutter wedging into the rock, the vibration and impact of the cutter, and the radial eccentric impact, cuts and breaks the rock, thereby increasing the rock-breaking force, quality, and efficiency. It is suitable for breaking hard rock. The combined effect of cutter vibration and eccentric impact rock-breaking also reduces the tunneling force required by the tunneling machine, lowering energy consumption. Simultaneously, reducing the tunneling force also reduces the reaction force exerted by the rock on the cutter, preventing cutter wear and failure, extending service life, and reducing the force transmitted from the cutter to the tunneling machine, thus preventing strong vibrations that could affect equipment stability and operational reliability. Attached Figure Description

[0043] Figure 1 This is a cross-sectional view of the rock-cutting mechanism of the present invention;

[0044] Figure 2 for Figure 1 Enlarged view of point C in the image;

[0045] Figure 3 for Figure 1 Enlarged view of point D in the image;

[0046] Figure 4 A cross-sectional view at point BB when the two planetary gears are symmetrically arranged about the first axis;

[0047] Figure 5 A cross-sectional view at point BB when the three planetary gears are arranged symmetrically about the first axis;

[0048] Figure 6 A cross-sectional view at point BB when the four planetary gears are arranged symmetrically about the first axis;

[0049] Figure 7 This is a cross-sectional view at point BB when the two planetary gears are 180° out of phase.

[0050] Figure 8 The diagram shows the inertial forces acting on the eccentric block after it rotates a certain angle when the two planetary gears are symmetrically arranged around the first axis (the eccentric block rotates from a solid structure to a hollow structure).

[0051] Figure 9 This is a force analysis diagram of the inertial force of the eccentric block after it rotates a certain angle when the two planetary gears are 180° out of phase (the eccentric block rotates from a solid structure to a hollow structure).

[0052] Figure 10This is a force analysis diagram of the inertial force of the eccentric block after it rotates a certain angle when the two planetary gears are 90° ahead of each other (the eccentric block rotates from a solid structure to a hollow structure).

[0053] Figure 11 This is a force analysis diagram of the inertial force after the eccentric block rotates by a certain angle when the two planetary gears are 90° out of phase (the eccentric block rotates from a solid structure to a hollow structure).

[0054] [Explanation of Labels in the Attached Image]

[0055] 1: Sun Gear;

[0056] 2: Planetary gears; 21: Eccentric structure;

[0057] 3: Planetary gear spindle;

[0058] 4: Planetary gear carrier; 41: Connecting shaft; 42: First limiting component; 43: Second limiting component; 44: Compression sleeve; 45: Quartered retaining ring; 46: Elastic retaining ring;

[0059] 5: Cutter head holder; 51: End cover; e: Second oil inlet.

[0060] 6: Knives;

[0061] 71: Housing; 711: Oil passage; a: Oil inlet; b: Oil outlet; c: Damping port; 712: Annular protrusion; 72: End plate; 721: Eccentric shaft; 73: Hydraulic oil injector;

[0062] 8: Sliding sleeve; d: First oil inlet passage;

[0063] 9: Sealing assembly; 91: Sealing seat; 92: Axial floating sealing sleeve; 93: Compressible expandable grease chamber; 94: Skeleton oil seal; 95: Limiting block;

[0064] 100: Rotation drive component; 101: Output shaft;

[0065] 201: Flat key; 202: First bearing; 203: Second bearing; 204: Third bearing; 205: Fourth bearing; 206: Pressure plate;

[0066] A: First axis. Detailed Implementation

[0067] To better explain and facilitate understanding of this invention, the terms "before" and "before" are used herein. Figure 1 The left-hand orientation in the middle is used as a reference, and "after" is used as... Figure 1 The right-hand orientation in the text is used as a reference.

[0068] See Figures 1-11As shown, the rock-cutting mechanism proposed in this embodiment of the invention includes a cutting tool assembly, which includes a sun gear 1, multiple planetary gears 2, a planetary gear spindle 3, a planetary gear carrier 4, a cutter head carrier 5, and a cutting tool 6.

[0069] The sun gear 1 is capable of rotating about a first axis A. Multiple planet gears 2 are arranged circumferentially around the first axis A and mesh with the sun gear 1, with an eccentric structure 21 mounted on them. A planet gear spindle 3 is used to mount and rotatably connect the planet gears 2, bearing the inertial torque and / or rotational radial inertial force transmitted by the multiple planet gears 2 as they alternately rotate around the first axis A. The planet gear carrier 4 is coaxial with the first axis A and is fixedly connected to the planet gear spindle 3. A cutter head 5 is movably connected to the planet gear carrier 4. When the planet gear carrier 4 alternately rotates around the first axis A, the cutter head 5 reciprocates along the first axis and / or synchronously alternates rotates around the first axis A; when the planet gear carrier 4 oscillates radially, the cutter head 5 synchronously oscillates radially. A cutter 6 is fixedly connected to the cutter head 5, and there is an eccentricity between the axis of the cutter 6 and the rotation center line of the cutter head 5.

[0070] The cutting method of this rock-breaking mechanism is as follows:

[0071] S1. The cutting tool 6 of the rock-breaking mechanism driven by the tunneling machine is driven into the rock.

[0072] S2. The sun gear 1 drives multiple planetary gears 2 to rotate synchronously around the first axis A and also rotate on their own axis. The planetary gears 2 transmit alternating inertial torque and / or radial inertial force to the planetary gear spindle 3 and the planetary gear carrier 4, driving the cutter head carrier 5 and the cutter 6 to reciprocate along the first axis (i.e., the direction of the first axis A), rotate alternatingly around the first axis A, reciprocating along the axis combined with radial oscillation, or rotate alternatingly combined with radial oscillation, so that the cutter 6 vibrates and impacts the rock in multiple motion trajectories to break the rock. During the process of vibrating and impacting the rock, the cutter 6 can also radially eccentrically impact and break the rock.

[0073] It should be noted that during the rotation of multiple planetary gears 2, the rotational position of their eccentric structures changes, and the direction of the dynamic load transmitted to the planetary gear carrier 4 changes accordingly, resulting in alternating motion directions of the tool holder 5 and the tool 6. Specifically, reciprocating movement along the first axis refers to forward and backward reciprocating movement along the first axis; alternating rotation around the first axis A refers to alternating clockwise and counterclockwise rotation around the first axis A; and rotational radial oscillation refers to radial oscillation with the oscillation direction rotating around the first axis A.

[0074] Based on the above configuration, this rock-breaking cutting mechanism drives multiple planetary gears 2 with eccentric structures 21 to revolve and rotate via a sun gear 1. The planetary gears 2 are mounted on a planetary gear carrier 4 via planetary gear spindles 3. The resultant force of the inertial forces generated by the eccentric structures 21 of the multiple planetary gears 2 acts on the planetary gear spindle 3, forming alternating inertial torque, radial inertial force, or a composite force of alternating inertial torque and radial inertial force. The alternating inertial torque can excite the planetary gear carrier 4 to rotate alternatingly around the first axis A; the radial inertial force can excite the planetary gear carrier 4 to oscillate radially; and the composite force of alternating inertial torque and radial inertial force can excite the planetary gear carrier 4 to perform a combined motion of alternating rotation and radial oscillation around the first axis A. The planetary gear carrier 4 can transmit dynamic loads to the cutterhead 5 connected to it: when the planetary gear carrier 4 rotates alternatingly around the first axis A, the cutterhead 5 reciprocates along the first axis and / or rotates synchronously around the first axis A. When the planetary gear carrier 4 oscillates radially, the cutterhead 5 oscillates synchronously along the radial direction. Furthermore, the tool holder 5 can drive the tool 6 to undergo axial reciprocating motion, circumferential alternating rotation, radial oscillation, a combination of axial reciprocating motion and radial oscillation, or a combination of circumferential alternating rotation and radial oscillation. At the same time, because there is an eccentricity between the axis of the tool 6 and the rotation center line of the tool holder 5, the tool 6 can also generate radial impact force during the movement.

[0075] Therefore, during the process of the cutting and rock-breaking mechanism driven by the tunneling machine to wedge into the rock, the cutting tool 6 can vibrate and impact the rock in a circumferential alternating rotation, radial oscillation, axial reciprocating movement, or a combination of circumferential and axial movements, or a combination of radial and axial movements. Furthermore, the cutting tool 6 can also radially eccentrically impact and break the rock. Under the combined effects of the squeezing and tunneling force of the cutting tool 6 wedging into the rock, the vibration and impact of the cutting tool, and the radial eccentric impact, the rock is cut and broken, thereby improving rock-breaking capacity (productivity), increasing rock-breaking efficiency, and reducing specific energy consumption. This mechanism is suitable for breaking hard rock. The auxiliary rock-breaking force from the cutting tool's vibration and eccentric impact also reduces the tunneling force required by the tunneling machine, thus reducing energy consumption. Simultaneously, reducing the tunneling force also reduces the reaction force exerted by the rock on the cutting tool 6, preventing wear and failure of the cutting tool 6, extending its service life, and reducing the force transmitted to the tunneling machine through the cutting tool 6, preventing strong vibrations of the entire machine from affecting equipment stability and operational reliability.

[0076] To further explain, due to the influence of the interaction pattern and state between the cutting tool 6 and the rock during the rock-breaking process, the vibration direction of the cutting tool 6 is uncertain, and its motion pattern is adaptive. When the equivalent load in the rock fracture direction is smaller, the vibration resistance of the cutting tool 6 in that direction is smaller, and the degree of vibration of the cutting tool 6 in that direction is greater, thus achieving rock fracture along the weaker surface. Conversely, when the equivalent load in the rock fracture direction is larger, it hinders the vibration of the cutting tool 6 in that direction. For example, when the equivalent load in the rock fracture direction on the first axis A is large, it will hinder the axial vibration of the cutting tool 6.

[0077] Furthermore, the eccentric structure 21 on the multiple planetary gears 2 has the following three configuration forms to transmit the inertial torque and / or rotational radial inertial force that alternately rotates about the first axis A to the planetary gear spindle 3.

[0078] The first configuration of the eccentric structure 21 is as follows: the eccentric structures 21 on multiple planetary gears 2 are symmetrically arranged around the first axis A, and the multiple planetary gears 2 can transmit the inertial torque of alternating rotation around the first axis A to the planetary gear spindle 3. The mechanism is as follows: See [link to relevant documentation]. Figure 8 As shown, taking two planetary gears 2 as an example, the inertial forces generated by the eccentric structures 21 on the multiple planetary gears 2 are balanced and canceled out in the vertical direction, while the horizontal component of the force forms a circumferential inertial torque acting on the planetary gear carrier 4. Since the planetary gears 2 continuously rotate on their own axis while revolving around the sun, the position of their eccentric center of mass continuously changes, causing the direction of the circumferential inertial torque to alternate between clockwise and counterclockwise.

[0079] The second configuration of the eccentric structure 21 is as follows: the eccentric structures 21 on adjacent planetary gears 2 are 180° out of phase, allowing multiple planetary gears 2 to transmit radial inertial force to the planetary gear spindle 3. The mechanism is as follows: (See...) Figure 9 As shown, taking two planetary gears 2 as an example, the eccentric structures 21 of each planetary gear 2 generate radial inertial forces when rotating. The directions of the radial inertial forces generated by each are consistent, and they can be superimposed and act on the planetary gear spindle 3. These forces act together on the planetary gear carrier 4, forming a single radial inertial force, the magnitude of which is n times the radial inertial force of a single eccentric structure 21, where n is the number of planetary gears 2. Since the planetary gears 2 continuously rotate on their own axis while revolving around the sun, the position of their eccentric centers of mass continuously changes, causing the direction of this combined inertial force to be non-fixed, but rather to rotate around the spindle, thus forming a rotational radial inertial force.

[0080] The third configuration of the eccentric structure 21 is as follows: the eccentric structures 21 on adjacent planetary gears 2 are 90° out of phase, allowing multiple planetary gears 2 to transmit alternating rotational inertial torque and radial inertial force to the planetary gear spindle 3. The mechanism is as follows: (See...) Figure 10 and Figure 11 As shown, taking two planetary gears 2 as an example, the phase difference of their eccentric structures is 90°, leading or lagging behind. The amplitude variation of their radial inertial force and circumferential inertial torque is consistent. When the eccentric structures 21 of multiple planetary gears 2 rotate, they generate inertial forces. The directions of the inertial forces generated by each are inconsistent, and the horizontal and vertical components cannot be balanced and canceled out. Their resultant force forms a radial inertial force that varies in magnitude and direction, and its magnitude is equal to the radial inertial force of a single eccentric structure 21. The number of planetary gears 2 is represented by n. Simultaneously, the centrifugal force generated by multiple eccentric structures 21 acts on different positions on the planetary gear carrier 4, thereby generating torque and forming an alternating rotational inertial torque. Thus, this arrangement can create a combined excitation effect of rotational radial inertial force and alternating circumferential inertial torque.

[0081] It should be noted that, see Figures 4-7 As shown, in this structural form, the number of planetary gears 2 is at least two.

[0082] Preferably, the planetary gear 2 has a receiving cavity, and the eccentric structure 21 is a lead block or lead powder disposed in the receiving cavity. The eccentric block and the planetary gear are an integral structure.

[0083] Because lead has a high density, lead blocks or lead powder are poured into planetary gear 2 to increase the mass of the same volume, thereby increasing the equivalent inertial mass and inertial excitation load per unit volume, which in turn increases the inertial eccentric force, thereby increasing the vibration force of the cutter 6 on the rock and improving the crushing efficiency.

[0084] Specifically, the center of mass of the eccentric structure 21 is symmetrical with respect to the tooth profile of the planetary gear 2, and the number of teeth on the planetary gear 2 is even. This further balances the radial inertial forces transmitted from the two planetary gears 2 to the planetary gear carrier 4 via the planetary gear spindle 3. The center of mass of the eccentric structure 21 is symmetrical with respect to the tooth profile of the planetary gear 2, and the number of teeth on the planetary gear 2 is an integer multiple of the number of planetary gears 2. When the number of planetary gears 2 is even, the number of teeth on both planetary gears 2 and the sun gear 1 is even. When the number of planetary gears is odd, the number of teeth on both planetary gears 2 and the sun gear 1 is odd. This ensures that the inertial forces generated by the rotation of multiple planetary gears 2 are balanced and canceled out.

[0085] Furthermore, the tool assembly also includes a rotation drive 100, the drive end of which is connected to the sun gear 1 for driving the sun gear 1 to rotate.

[0086] Optionally, the rotation drive 100 is a hydraulic motor.

[0087] Furthermore, this rock-breaking mechanism also includes a housing 71, inside which a cutter assembly is provided to support the cutter assembly and to connect to the tunneling machine to drive the cutter 6 to wedge into the rock and break it.

[0088] Specifically, the rear end of the housing 71 is fixedly connected to the end plate 72, and the end plate 72 is sleeved on the outer periphery of the output shaft 101 of the rotation drive 100.

[0089] Specifically, the main body of the rotation drive 100 is connected to the end plate 72 by screws, and the output shaft 101 of the rotation drive 100 is connected to the sun gear 1 by a flat key 201 to drive the sun gear 1 to rotate. The output shaft 101 is rotatably connected to the end plate 72 by a first bearing 202.

[0090] The connecting shaft of the sun gear 1 is inserted into the planetary gear carrier 4. A second bearing 203 is provided between the outer circumference of the connecting shaft and the planetary gear carrier 4 to support the rotation of the sun gear 1. A third bearing 204 is provided between the inner circumference of the planetary gear 2 and the planetary gear spindle 3 to support the rotation of the planetary gear 2 around the planetary gear spindle 3. The planetary gear spindle 3 is inserted into the planetary gear carrier 4. A fourth bearing 205 is provided between the outer circumference of the planetary gear carrier 4 and the outer casing 71 to support the rotation of the planetary gear carrier 4 relative to the outer casing 71. The front end of the cutter head holder 5 has a wedge-shaped surface, which is used to cooperate with the wedge-shaped surface at the rear end of the cutter 6 for positioning. The cutter head holder 5 is fixedly connected to the cutter 6 by screws. The front end of the cutter head holder 5 is also fixedly connected to the end cap 51 by screws, and the end cap 51 is used to close the front end opening of the cutter head holder 5.

[0091] Furthermore, the connection method between the planetary gear carrier 4 and the cutter head 5 is as follows:

[0092] The planetary gear carrier 4 has a connecting shaft 41 at its front end. The rear end of the cutter head carrier 5 is sleeved on the connecting shaft 41 and connected to the connecting shaft 41 through a lead screw and nut structure or an internal and external helical gear structure.

[0093] When the planetary gear carrier 4 carries the alternating inertial torque and rotates alternately around the first axis A, the connecting shaft 41 of the planetary gear carrier 4 drives the cutter head 5 to reciprocate along the first axis and / or rotate synchronously around the first axis A through the lead screw and nut structure or the internal and external helical gear structure.

[0094] During the process of the cutter 6 wedging into the rock, when the equivalent load on the rock's fracture direction along the first axis A is large and hinders the axial movement of the cutter, the cutter head 5 is axially locked, and the alternating rotation of the planetary gear carrier 4 will drive the cutter head 5 to rotate synchronously. When the equivalent load on the rock's fracture direction around the first axis A is large and hinders the rotation of the cutter, the cutter head 5 is circumferentially restricted by the load, and the alternating rotation of the planetary gear carrier 4 will drive the cutter head 5 to move synchronously axially reciprocatingly.

[0095] Specifically, the peripheral wall of the connecting shaft 41 is provided with a lead screw or an external helical tooth, and the inner periphery of the cutter head holder 5 is provided with a matching lead screw or an internal helical tooth.

[0096] Specifically, in order to limit the axial movement of the cutter head 5, a first limiting member 42 and a second limiting member 43 are provided at intervals along the first axial direction on the outer periphery of the planetary gear carrier 4, so that the cutter head 5 can move along the first axial direction to abut against the first limiting member 42 or the second limiting member 43.

[0097] More specifically, the journal of the connecting shaft 41 is provided with a first annular groove and a second annular groove at intervals from back to front along the first axial direction. The first limiting member 42 is a thrust bearing sleeved on the first collar.

[0098] A four-part retaining ring 45 is inserted into the first annular groove, and the four-part retaining ring 45 abuts against the end face of the first limiting member 42. An elastic retaining ring 46 is inserted into the second annular groove. A retaining sleeve 44 is fitted onto the journal between the four-part retaining ring 45 and the elastic retaining ring 46, and the inner circumference of the retaining sleeve 44 abuts against the outer circumference of the four-part retaining ring 45 and the first limiting member 42. The axial movement of the first limiting member 42 is restricted by the cooperation of the retaining sleeve 44, the four-part retaining ring 45 and the elastic retaining ring 46, and the first limiting member 42 is easily installed and removed.

[0099] The second limiting member 43 is a thrust bearing sleeved on the outer periphery of the planetary gear carrier 4.

[0100] More specifically, both the first limiting member 42 and the second limiting member 43 are axial limiting thrust bearings.

[0101] More specifically, the inner circumference of the cutter head holder 5 is provided with a convex ring. The cutter head holder 5 can move axially forward until the convex ring abuts against the rear end of the first limiting member 42, and the cutter head holder 5 can also move axially backward until the rear end abuts against the second segment member.

[0102] Furthermore, to accommodate the axial movement and rotation of the tool holder 5, a sliding sleeve 8 is provided between the outer periphery of the tool holder 5 and the inner wall of the outer casing 71. The sliding sleeve 8 is used to support the axial movement and rotation of the tool holder 5.

[0103] Specifically, the outer circumference of the sliding sleeve 8 has a transition fit with the outer shell 71, while the inner circumference has a clearance fit with the cutter head holder. The sliding sleeve 8 is equivalent to a sliding bearing.

[0104] Preferably, to prevent dust from entering the sliding sleeve 8 during rock crushing, this embodiment further specifies:

[0105] The front end of the cutter head holder 5 extends out of the front end of the housing 71. A sealing assembly 9 is fixedly installed at the front end of the housing 71. The sealing assembly 9 is located on the front side of the sliding sleeve 8. The sealing assembly 9 includes a sealing seat 91, an axially floating sealing sleeve 92, a compressible expandable grease chamber 93, and a skeleton oil seal 94.

[0106] A first sealing groove and a second sealing groove are sequentially formed along the inner circumference of the sealing seat 91 from front to back along the first axial direction. An axially floating sealing sleeve 92 and a compressible expandable grease chamber 93 are disposed within the first sealing groove. The axially floating sealing sleeve 92 and the cutter head holder 5 are in clearance fit. The rear end of the axially floating sealing sleeve 92 presses against the compressible expandable grease chamber 93, which contains and discharges grease under pressure. A skeleton oil seal 94 is disposed within the second sealing groove.

[0107] When grease is injected into the compressible expandable grease chamber 93, the axial floating seal sleeve 92 can axially squeeze the compressible expandable grease chamber 93 to discharge the grease. The grease enters the gap between the axial floating seal sleeve 92 and the cutter head 5 to form a pressure expansion effect of the grease, which prevents external dust from entering and prevents dust-laden grease from entering the sliding sleeve 8. This is more conducive to ensuring the sealing working conditions of the skeleton oil seal 94. The skeleton oil seal 94 can prevent hydraulic oil from entering the sliding sleeve 8, thereby improving the sealing effect of dust sealing and oil sealing, and realizing the combined effect of comprehensive dust sealing and oil sealing.

[0108] Specifically, the inner circumference of the axial floating seal sleeve 92 has a stepped spiral annular groove, into which grease can enter and form a grease pressure zone with the outer circumference of the cutter head holder 5.

[0109] Specifically, the sealing seat 91 has an oil passage that connects to the oil inlet a of the compressible expandable grease chamber 93. The oil passage can be connected to an external oil injector to inject grease into the compressible expandable grease chamber 93.

[0110] Specifically, to achieve axial positioning of the axial floating sealing sleeve 92, this embodiment further defines:

[0111] The sealing assembly 9 also includes a limiting block 95 disposed on the sealing seat 91. The limiting block 95 is located above the axial floating sealing sleeve 92. The protrusion at the bottom of the limiting block 95 is inserted into the axial limiting groove at the top of the axial floating sealing sleeve 92. The axial floating sealing sleeve 92 can move axially to the axial limiting groove and abut against both sides of the protrusion.

[0112] Specifically, a pressure plate 206 is provided between the rear end of the sealing seat 91 and the front end of the housing 71, and an annular protrusion 712 is provided on the inner circumference of the housing 2 behind the sliding sleeve 8, so as to limit the axial movement position of the sliding sleeve 8 by means of the pressure plate 206 and the annular protrusion 712.

[0113] Furthermore, to achieve lubrication of the tool assembly, this embodiment further specifies:

[0114] An axially extending oil passage 711 is provided on the outer casing 71. The oil inlet a of the oil passage 711 is used to connect to the built-in hydraulic oil injector 73 or the external grease gun, and the oil passage 711 is provided with multiple oil outlets b.

[0115] The slide sleeve 8 is provided with multiple first oil inlet channels d that connect the outer periphery of the slide sleeve 8 and the outer shell 71, and connect the inner periphery of the slide sleeve 8 and the cutter head holder 5. The first oil inlet channels d are connected to the oil outlet b, so as to achieve lubrication of the inner and outer peripheries of the slide sleeve 8 with lubricating oil or grease and hydrostatic support.

[0116] The cutter head 5 has a second oil inlet channel e with a damping hole c. One end of the second oil inlet channel e is connected to the first oil inlet channel d, and the other end is connected to the connection part of the cutter head 5 and the planetary gear carrier 4 to form back pressure, so that the lubricating oil is discharged into the lead screw nut or the internal and external helical gear connection part through the damping hole c to form forced lubrication, so as to achieve forced, quantitative, continuous and efficient lubrication.

[0117] The hydraulic oil injector 73 is located on the end plate 72 and can inject lubricating oil into the oil inlet a, while the external grease gun can inject lubricating grease into the oil inlet a.

[0118] Specifically, the sun gear meshes with two stages of gears. Driven by the rotating drive component 100, the sun gear, after being reduced in speed by the two stages of gears, can drive the built-in hydraulic oil injector 73 to inject lubricating oil into the oil inlet a.

[0119] Two-stage gears are mounted on an eccentric shaft 721, which is rotatably connected to the end plate 72 via bearings.

[0120] Specifically, when grease lubrication is required, the screw plug in the threaded blind hole on the housing 71 is removed and replaced with a grease injection nozzle to connect to the grease injection gun, and grease is injected into the oil inlet a.

[0121] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part. They can refer to a mechanical connection or an electrical connection. They can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. For those skilled in the art, the specific meaning of the above terms in this invention can be understood according to the specific circumstances.

[0122] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first and second features are in direct contact, or that they are in indirect contact through an intermediate medium. Furthermore, "above," "over," or "on top" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," or "beneath" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0123] In the description of this specification, the terms "one embodiment," "some embodiments," "embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0124] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make modifications, alterations, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A rock-cutting mechanism, characterized in that, The tool assembly comprises: a sun gear (1) capable of rotating around a first axis (A); a plurality of planet gears (2) arranged circumferentially around the first axis (A) and engaged with the sun gear (1), and provided with eccentric structures (21) thereon; a planet gear shaft (3) for sleeving and rotatingly connecting the planet gears (2) to bear the inertial torque and / or the rotational radial inertia force of the planet gears (2) transmitted around the first axis (A); a planet gear carrier (4) coaxial with the first axis (A) and fixedly connected with the planet gear shaft (3); a cutter carrier (5) movably connected with the planet gear carrier (4), and reciprocally moving along the first axis and / or rotating around the first axis (A) when the planet gear carrier (4) rotates around the first axis (A), and rotating radially when the planet gear carrier (4) swings radially; a tool (6) fixedly connected with the cutter carrier (5) and having an eccentricity with the rotation center line of the cutter carrier (5).

2. The rock breaking mechanism according to claim 1, wherein: the eccentric structures (21) on the plurality of planet gears (2) are symmetrically arranged around the first axis (A), and the plurality of planet gears (2) are capable of transmitting the inertial torque of the planet gears (2) rotating around the first axis (A) to the planet gear shaft (3); or the eccentric structures (21) on adjacent planet gears (2) are 180° out of phase, and the plurality of planet gears (2) are capable of transmitting the rotational radial inertia force to the planet gear shaft (3); or the eccentric structures (21) on adjacent planet gears (2) are 90° out of phase, and the plurality of planet gears (2) are capable of transmitting the inertial torque of the planet gears (2) rotating around the first axis (A) and the rotational radial inertia force to the planet gear shaft (3).

3. The cutting rock fragmentation mechanism of claim 1 or 2, wherein, The planet gears (2) are provided with accommodating cavities, and the eccentric structures (21) are lead blocks or lead powder arranged in the accommodating cavities.

4. The cutting rock fragmentation mechanism of claim 1, wherein, The planet gear carrier (4) is provided with a connecting shaft (41) at the front end thereof; the rear end of the cutter carrier (5) is sleeved on the connecting shaft (41) and connected with the connecting shaft (41) through a screw-nut structure or an internal-external helical gear structure; the first limiting member (42) and the second limiting member (43) are arranged along the first axis at the outer periphery of the planet gear carrier (4), and the cutter carrier (5) can be moved along the first axis to abut against the first limiting member (42) or the second limiting member (43).

5. The rock breaking mechanism according to claim 4, wherein: the first limiting member (42) is a thrust bearing sleeved on the front end of the connecting shaft (41). The shaft journal is spaced apart by a first ring groove and a second ring groove from back to front along the first axis; a quarter split ring (45) is inserted into the first ring groove, and the quarter split ring (45) abuts against the end face of the first limiting part (42); an elastic check ring (46) is inserted into the second ring groove, and a sleeve (44) is sleeved on the shaft journal between the quarter split ring (45) and the elastic check ring (46), and the inner periphery of the sleeve (44) abuts against the outer periphery of the quarter split ring (45) and the first limiting part (42); The second limiting part (43) is a thrust bearing sleeved on the outer periphery of the planet carrier (4).

6. The cutting rock fragmentation mechanism of claim 1, wherein, Further comprising a housing (71) internally provided with the cutter assembly; A sliding sleeve (8) is arranged between the outer periphery of the cutter holder (5) and the inner wall of the housing (71), and the sliding sleeve (8) is used to support the axial movement and rotation of the cutter holder (5).

7. The cutting rock fragmentation mechanism of claim 6, wherein, The front end of the cutter holder (5) protrudes from the front end of the housing (71), and a sealing assembly (9) is fixedly arranged at the front end of the housing (71), the sealing assembly (9) is located on the front side of the sliding sleeve (8), and the sealing assembly (9) comprises: A sealing seat (91) is internally provided with a first sealing groove and a second sealing groove in sequence from front to back along the first axis; An axially floating sealing sleeve (92) and a compressible and expandable grease chamber (93) are arranged in the first sealing groove, the axially floating sealing sleeve (92) is in clearance fit with the cutter holder (5), the rear end of the axially floating sealing sleeve (92) abuts against the compressible and expandable grease chamber (93), and the compressible and expandable grease chamber (93) contains and discharges lubricating grease when compressed; and a skeleton oil seal (94) arranged in the second sealing groove; When the compressible and expandable grease chamber (93) is filled with lubricating grease, the axially floating sealing sleeve (92) can extrude the compressible and expandable grease chamber (93) to discharge lubricating grease.

8. The cutting rock breaking mechanism of claim 7, wherein, An oil channel (711) extending along the axis is arranged on the housing (71); an oil inlet (a) of the oil channel (711) is used to connect an internal hydraulic oil injection device (73) or an external grease injection gun, and a plurality of oil outlets (b) are arranged on the oil channel (711); A plurality of first oil inlets (d) are arranged on the sliding sleeve (8), and the first oil inlets (d) are connected between the outer periphery of the sliding sleeve (8) and the housing (71) and between the inner periphery of the sliding sleeve (8) and the cutter holder (5); and the first oil inlets (d) are connected with the oil outlets (b); A second oil inlet (e) with a damping hole is arranged on the cutter holder (5), one end of the second oil inlet (e) is connected with the first oil inlet (d), and the other end of the second oil inlet (e) is connected with the connection part of the cutter holder (5) and the planet carrier (4).

9. The cutting rock fragmentation mechanism of claim 1, wherein, The cutter assembly further comprises a rotation driving part (100), and a driving end of the rotation driving part (100) is connected with the sun gear (1) to drive the sun gear (1) to rotate.

10. A cutting method for the cutting rock-breaking mechanism according to any one of claims 1-9, characterized in that, The cutting method is S1, the cutter (6) of the cutting rock breaking mechanism is wedged into the rock by the heading machine; S2, the sun gear (1) drives a plurality of the planetary gears (2) to synchronously rotate around the first axis (A) and to rotate on their own axes, the planetary gears (2) transmit the alternating inertial torque and / or the radial inertial force to the planetary wheel shaft (3) and the planetary wheel carrier (4), drive the cutter holder (5) and the cutter (6) to reciprocate along the first axis, to alternately rotate around the first axis (A), to reciprocate along the first axis combined with the radial swing, or to alternately rotate combined with the radial swing, so that the cutter (6) vibrates and impacts to break the rock; in the process of vibrating and impacting to break the rock, the cutter (6) can also radially eccentrically impact to break the rock.

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