阅读说明：本技术 摇摆制动式减速装置、风力发电机的摇摆制动式制动系统 (Swing brake type speed reducer and swing brake type brake system of wind driven generator ) 是由 李和良 吴伟明 许凯杰 陈幸 郦先苗 于 2020-12-29 设计创作，主要内容包括：本发明涉及摇摆制动式减速装置、风力发电机的摇摆制动式制动系统。摇摆制动式减速装置,包括：传动齿轮、摇摆式传动转轴及摇摆式连杆,所述摇摆式传动转轴与所述传动齿轮连接,所述摇摆式连杆与所述摇摆式传动转轴连接；所述摇摆制动式减速装置还包括壳体,所述壳体开设有第一弧形引导槽及第二弧形引导槽,所述摇摆式连杆的两端分别设置有第一球头和第二球头；所述摇摆制动式减速装置还包括第一传动连杆、第二传动连杆、第一活塞及第二活塞。本发明公开的摇摆制动式减速装置、风力发电机的摇摆制动式制动系统,当风力过大时自动进入制动状态,从而对风力发电机进行减速,避免风力发电机超负荷运行,从而延长风力发电机的使用寿命。(The invention relates to a swing brake type speed reducer and a swing brake type brake system of a wind driven generator. A rocking brake type reduction gear comprising: the swing type transmission device comprises a transmission gear, a swing type transmission rotating shaft and a swing type connecting rod, wherein the swing type transmission rotating shaft is connected with the transmission gear, and the swing type connecting rod is connected with the swing type transmission rotating shaft; the swing brake type speed reducer further comprises a shell, the shell is provided with a first arc-shaped guide groove and a second arc-shaped guide groove, and a first ball head and a second ball head are respectively arranged at two ends of the swing type connecting rod; the swing brake type speed reducing device further comprises a first transmission connecting rod, a second transmission connecting rod, a first piston and a second piston. The swing brake type speed reducing device and the swing brake type braking system of the wind driven generator disclosed by the invention automatically enter a braking state when wind power is too large, so that the wind driven generator is decelerated, the overload operation of the wind driven generator is avoided, and the service life of the wind driven generator is prolonged.)

1. A rocking brake type reduction gear, comprising: the swing type transmission device comprises a transmission gear, a swing type transmission rotating shaft and a swing type connecting rod, wherein the swing type transmission rotating shaft is connected with the transmission gear, and the swing type connecting rod is connected with the swing type transmission rotating shaft;

the swing brake type speed reducer further comprises a shell, wherein a first arc-shaped guide groove and a second arc-shaped guide groove are formed in the shell, a first ball head and a second ball head are respectively arranged at two ends of the swing type connecting rod, the first ball head is slidably clamped in the first arc-shaped guide groove, and the second ball head is slidably clamped in the second arc-shaped guide groove;

the swing brake type speed reducing device also comprises a first transmission connecting rod, a second transmission connecting rod, a first piston and a second piston; one end of the swing connecting rod is hinged with one end of the first connecting rod, and the other end of the first connecting rod is hinged with the first piston; the other end of the swing connecting rod is hinged with one end of the second transmission connecting rod, and the other end of the second transmission connecting rod is hinged with the second piston;

the shell is further provided with a first gas cavity and a second gas cavity, the first gas cavity is provided with a first one-way air inlet valve and a first one-way air outlet valve, and the second gas cavity is provided with a second one-way air inlet valve and a second one-way air outlet valve; the first piston is slidably disposed in the first gas chamber, and the second piston is slidably disposed in the second gas chamber.

2. The rocking brake type deceleration device of claim 1, wherein the first one-way outlet valve is externally connected to a first air reservoir.

3. The rocking brake type deceleration device of claim 1, wherein the second one-way outlet valve is externally connected to a second air reservoir.

4. The rocking brake reduction gear of claim 1, wherein the rocking drive shaft comprises: the device comprises a rotating connecting rod part, a swinging piece, a first eccentric dislocation piece, a second eccentric dislocation piece and a matching connecting rod part, wherein the rotating connecting rod part is eccentrically connected with one end of the swinging piece in a dislocation way through the first eccentric dislocation piece; the matching connecting rod part is eccentrically connected with the other end of the swinging piece in a staggered manner through the second eccentric staggered piece; the rotating connecting rod part is further connected with the transmission gear, and the matching connecting rod part is further rotatably arranged on the shell.

5. The rocking brake type deceleration device according to claim 1, wherein the first piston is a cylindrical structure.

6. The rocking brake type deceleration device according to claim 1, wherein the second piston is a cylindrical structure.

7. A rocking brake type braking system of a wind power generator, comprising a rocking brake type decelerating device as claimed in any one of claims 1 to 6;

the swing braking type braking system of the wind driven generator further comprises a wind power induction driving device, and the swing braking type speed reducing device is in driving connection with the wind power induction driving device.

Technical Field

The invention relates to the technical field of wind driven generators, in particular to a swing brake type speed reducing device and a swing brake type brake system of a wind driven generator.

Background

Wind power generation is a process of converting wind energy into mechanical energy and then converting the mechanical energy into electric energy. The process does not need fuel, does not radiate, does not pollute the air and the environment, and therefore, the wind energy is clean energy.

However, the wind power input to the wind power generation apparatus is not artificially set, but is a magnitude of natural wind depending on the working environment in which the wind power generation apparatus is located, that is, a magnitude of wind power driving the wind power generation apparatus is not controllable. At present, the wind power generators on the market are easy to run under overload due to overlarge wind power, and finally, the wind power generation equipment is overloaded and burnt out.

Of course, when the wind power of the wind power generation equipment is too large, the protection function is started to protect the wind power generation equipment and prevent the wind power generation equipment from being burnt out due to overload operation. For example, in the invention patent with publication number CN104500337A, when the wind force is too large, the worker needs to manually operate the handle to start the protection mechanism to realize the protection function. Through a manual protection mechanism, on one hand, the wind power needs to be monitored in real time, and the labor cost is high; on the other hand, since the worker knows that the wind force is too large, a certain time is required for the worker to manually complete the protection operation of the protection mechanism, and in this time period, the wind power generation equipment is in an overload state. Therefore, the wind power generation equipment inevitably has an overload state, and thus the protection effect of the wind power generation equipment is not ideal.

Disclosure of Invention

The invention aims to overcome the defects in the prior art and provide a swing brake type speed reducing device and a swing brake type braking system of a wind driven generator.

The purpose of the invention is realized by the following technical scheme:

a rocking brake type deceleration device comprising: the swing type transmission device comprises a transmission gear, a swing type transmission rotating shaft and a swing type connecting rod, wherein the swing type transmission rotating shaft is connected with the transmission gear, and the swing type connecting rod is connected with the swing type transmission rotating shaft;

the swing brake type speed reducer further comprises a shell, wherein a first arc-shaped guide groove and a second arc-shaped guide groove are formed in the shell, a first ball head and a second ball head are respectively arranged at two ends of the swing type connecting rod, the first ball head is slidably clamped in the first arc-shaped guide groove, and the second ball head is slidably clamped in the second arc-shaped guide groove;

the swing brake type speed reducing device also comprises a first transmission connecting rod, a second transmission connecting rod, a first piston and a second piston; one end of the swing connecting rod is hinged with one end of the first transmission connecting rod, and the other end of the first transmission connecting rod is hinged with the first piston; the other end of the swing connecting rod is hinged with one end of the second transmission connecting rod, and the other end of the second transmission connecting rod is hinged with the second piston;

the shell is further provided with a first gas cavity and a second gas cavity, the first gas cavity is provided with a first one-way air inlet valve and a first one-way air outlet valve, and the second gas cavity is provided with a second one-way air inlet valve and a second one-way air outlet valve; the first piston is slidably disposed in the first gas chamber, and the second piston is slidably disposed in the second gas chamber.

In one embodiment, the first one-way outlet valve is externally connected with the first air reservoir.

In one embodiment, the second one-way outlet valve is externally connected to the second air reservoir.

In one embodiment, the rocking drive shaft comprises: the device comprises a rotating connecting rod part, a swinging piece, a first eccentric dislocation piece, a second eccentric dislocation piece and a matching connecting rod part, wherein the rotating connecting rod part is eccentrically connected with one end of the swinging piece in a dislocation way through the first eccentric dislocation piece; the matching connecting rod part is eccentrically connected with the other end of the swinging piece in a staggered manner through the second eccentric staggered piece; the rotating connecting rod part is further connected with the transmission gear, and the matching connecting rod part is further rotatably arranged on the shell.

In one embodiment, the first piston is a cylinder structure.

In one embodiment, the second piston is a cylindrical structure.

The invention also discloses a swing braking type braking system of the wind driven generator, which comprises the swing braking type speed reducing device;

the swing braking type braking system of the wind driven generator further comprises a wind power induction driving device, and the swing braking type speed reducing device is in driving connection with the wind power induction driving device.

The swing brake type speed reducing device and the swing brake type braking system of the wind driven generator disclosed by the invention automatically enter a braking state when wind power is too large, so that the wind driven generator is decelerated, the overload operation of the wind driven generator is avoided, and the service life of the wind driven generator is prolonged.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.

FIG. 1 is a schematic view (one) of the structure of a rocking brake type reduction gear of the present invention;

FIG. 2 is a schematic view (two) of the structure of the rocking brake type reduction gear of the present invention;

FIG. 3 is a schematic view of a portion of the wobble brake deceleration assembly shown in FIG. 2;

FIG. 4 is an exploded view of the rocking brake reduction gear of FIG. 3;

FIG. 5 is a schematic structural view of a rolling brake type braking system of a wind power generator according to the present invention;

FIG. 6 is a partial schematic structural view of a rocking brake type braking system of the wind turbine shown in FIG. 5;

FIG. 7 is a schematic structural view of the wind induction drive unit shown in FIG. 5;

FIG. 8 is a schematic view of the connection of the wind sensing assembly shown in FIG. 7 to the brake release assembly.

Detailed Description

To facilitate an understanding of the invention, the invention will now be described more fully with reference to the accompanying drawings. Preferred embodiments of the present invention are shown in the drawings. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete.

It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "left," "right," and the like as used herein are for illustrative purposes only and do not represent the only embodiments.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

As shown in fig. 1, the present invention discloses a rocking brake type reduction gear 10, comprising: transmission gear 100, rocking transmission pivot 200 and rocking connecting rod 300, rocking transmission pivot 200 is connected with transmission gear 100, and rocking connecting rod 300 is connected with rocking transmission pivot 200.

As shown in fig. 1 and fig. 2, specifically, the swing brake type speed reducer 10 further includes a housing 101, the housing 101 is provided with a first arc-shaped guiding groove 400 and a second arc-shaped guiding groove 500, two ends of the swing type connecting rod 300 are respectively provided with a first ball head 310 and a second ball head 320, the first ball head 310 is slidably engaged with the first arc-shaped guiding groove 400, and the second ball head 320 is slidably engaged with the second arc-shaped guiding groove 500.

As shown in fig. 2, specifically, the rocking brake type reduction gear 10 further includes a first transmission link 600, a second transmission link 700, a first piston 800 and a second piston 900; one end of the rocking link 300 is hinged to one end of the first transmission link 600, and the other end of the first transmission link 600 is hinged to the first piston 800. The other end of the rocking link 300 is hinged to one end of the second transmission link 700, and the other end of the second transmission link 700 is hinged to the second piston 900.

As shown in fig. 2, in detail, the housing 101 further defines a first gas chamber 102 and a second gas chamber 103, the first gas chamber 102 is provided with a first one-way inlet valve 104 and a first one-way outlet valve 105, and the second gas chamber 103 is provided with a second one-way inlet valve 106 and a second one-way outlet valve 107. The first piston 800 is slidably disposed in the first gas chamber 102 and the second piston 900 is slidably disposed in the second gas chamber 103.

Specifically, the first one-way gas outlet valve 105 is externally connected to a first gas storage cylinder (not shown). The second one-way outlet valve 107 is externally connected to a second air reservoir (not shown).

As shown in fig. 3 and 4, in detail, the swing type transmission shaft 200 includes: the rotating connecting rod part 210, the swinging part 220, the first eccentric displacement part 230, the second eccentric displacement part 240 and the matching connecting rod part 250, wherein the rotating connecting rod part 210 and one end of the swinging part 220 are eccentrically connected in a displacement way through the first eccentric displacement part 230. The engagement link portion 250 is eccentrically offset-coupled to the other end of the rocking member 220 by the second eccentric offset member 240. The rotating link portion 210 is further connected to the transmission gear 100, and the mating link portion 250 is further rotatably disposed in the housing 101.

Specifically, the first piston 800 has a cylindrical structure, and the second piston 900 has a cylindrical structure.

The operation of the swing brake type reduction gear 10 will be described below (see fig. 1 to 4 together):

when the transmission gear 100 rotates, the swinging type transmission rotating shaft 200 is driven to rotate, and when the swinging type transmission rotating shaft 200 rotates in a swinging manner, the swinging type connecting rod 300 is driven to swing in a reciprocating manner within a certain angle range; during the reciprocating swing process of the swing type connecting rod 300, the first ball head 310 reciprocates along the first arc-shaped guide groove 400, and the second ball head 320 reciprocates along the second arc-shaped guide groove 500; meanwhile, when the rocking link 300 is rocked back and forth within a certain angle range, the first and second driving links 600 and 700 are alternately pushed and pulled back and forth, thereby indirectly alternately pushing and pulling the first and second pistons 800 and 900;

it should be noted that when one end of the rocking connecting rod 300 pulls the first piston 800 away from the first one-way intake valve 104, the gas outside the housing 101 enters the first gas chamber 102 through the first one-way intake valve 104; meanwhile, the other end of the swing connecting rod 300 pushes the second piston 900 towards the direction close to the second one-way gas outlet valve 107, so that the gas in the second gas cavity 103 enters the second gas reservoir from the second one-way gas outlet valve 107;

similarly, when one end of the rocking link 300 pushes the first piston 800 in a direction close to the first one-way vent valve 105, the gas in the first gas chamber 102 enters the first gas reservoir through the first one-way vent valve 105; meanwhile, the other end of the rocking connecting rod 300 pulls the second piston 900 away from the second one-way intake valve 106, so that the gas outside the housing 101 enters the first gas cavity 102 through the second one-way intake valve 106;

the swinging brake type speed reducer 10 of the present invention converts the rotary motion into the reciprocating swing of the pendulum type, and then converts the reciprocating swing of the pendulum type into the reciprocating linear motion, and finally realizes the alternate suction and discharge of the gas in the first gas chamber 102 and the second gas chamber 103.

As shown in fig. 5, the invention further discloses a swing brake type braking system 20 of the wind driven generator, which comprises a swing brake type speed reducer 10 and a wind induction driving device 30, wherein the swing brake type speed reducer 10 is in driving connection with the wind induction driving device 30.

As shown in fig. 5, specifically, the wind induction driving apparatus 30 includes: the wind power induction assembly 40 is connected with the braking unlocking assembly 50, the braking unlocking assembly 50 is in contact with or separated from the wind power braking assembly 60, and the swing braking type speed reducing device 10 is in driving connection with the wind power braking assembly 60.

As shown in fig. 5, in particular, the wind induction assembly 40 includes: a sail (not shown), a free link 401, a guide base 402, a free slider 403 and a transmission return spring 404; the sail is connected with a free slide block 403 through a free connecting rod 401; a free slider 403 is slidably disposed on the guide base 402; one end of the transmission return spring 404 is connected to the free slider 403, and the other end is connected to the guide base 402.

As shown in fig. 7 and 8, specifically, the braking unlocking assembly 50 includes a supporting link 501 and a V-shaped transmission member 502, and the V-shaped transmission member 502 is rotatably sleeved on the supporting link 501; the V-shaped transmission member 502 has a displacement sensing end 503, the free sliding block 403 has a stepped guiding groove 405, and the displacement sensing end 503 is slidably engaged with the stepped guiding groove 405. The displacement sensing end 503 is provided with a third ball 504, and the third ball 504 is slidably engaged in the stepped guide groove 405.

As shown in fig. 6 and 7, specifically, the wind brake assembly 60 includes: the brake ratchet 601, the brake gear 602, the brake release member 603 and the brake connecting rod 604, the brake ratchet 601 is connected with the brake connecting rod 604 in a driving manner, the brake gear 602 is movably sleeved on the brake connecting rod 604, and the brake gear 602 is meshed with the transmission gear 100. The brake unlocking piece 603 is rotatably arranged on the brake gear 602, the V-shaped transmission piece 502 is also provided with a brake locking end 505, and the brake unlocking piece 603 is locked with the brake locking end 505 or the brake ratchet 601.

As shown in fig. 7, in particular, the wind power brake assembly 60 further includes a limiting elastic sheet 605, and the limiting elastic sheet 605 is disposed on the brake gear 602 and abuts against the brake unlocking piece 603, so that the brake unlocking piece 603 has a tendency to be locked with the brake ratchet 601. It should be noted that the limiting elastic sheet 605 abuts against the braking unlocking piece 603, so that the braking unlocking piece 603 has a tendency of locking with the braking ratchet 601; that is, the limit elastic sheet 605 provides a supporting force for the braking unlocking piece 603, so that the gravity of the braking unlocking piece 603 is overcome, the braking unlocking piece 603 is stably locked with the braking ratchet 601, and unhooking is prevented; thereby ensuring stability of the brake system 20 and providing reliable brake protection for the wind turbine.

Specifically, as shown in fig. 7, the brake release member 603 has a lock engaging end 606 and a linkage lock end 607, the lock engaging end 606 being locked to or separated from the brake lock end 505; the linkage locking end 607 is locked or separated with the brake ratchet 601.

As shown in fig. 7, in particular, the linkage locking end 607 has a hook 608, and the hook 608 is locked with or separated from a ratchet groove 609 of the braking ratchet 601. Through the structural cooperation of the hook 608 and the ratchet groove 609, on one hand, the linkage locking end 607 and the braking ratchet 601 are ensured to be easily locked; on the other hand, the linkage locking end 607 is easy to separate from the braking ratchet 601; thereby ensuring reliability and stability of the brake system 20.

As shown in fig. 8, in detail, the guide base 402 is provided with a linear guide groove 406, and the free slider 403 is slidably disposed along the linear guide groove 406.

When the swing brake type braking system 20 of the wind power generator of the present invention is applied to a wind power generator, the brake link 604 is connected to a transmission shaft of the wind power generator. It should be particularly noted that the fan blade is connected to the wind driven generator through the brake link 604, that is, the fan blade drives the transmission shaft of the wind driven generator to rotate through the brake link 604, so as to realize the power generation of the wind driven generator.

The invention discloses a swing brake type braking system 20 of a wind driven generator, which is applied to the technical field of wind driven generators; when the wind power around the wind driven generator exceeds a preset limit value, the wind driven generator is braked, so that the wind driven generator is prevented from being overloaded to run and shorten the service life or burn out.

The operation principle of the rolling brake type braking system 20 of the wind turbine generator will be described below (please refer to fig. 5 to 8):

firstly, setting an overload limit value aiming at the load capacity of the wind driven generator, and when the wind power does not exceed the overload limit value, the braking system 20 is in a non-braking state, and the wind driven generator normally runs to generate electricity; when the wind power exceeds the overload limit value, the braking system 20 enters a braking state, and the braking system 20 decelerates a transmission shaft of the wind driven generator; the generator is prevented from being burnt out due to the over-high rotating speed of the transmission shaft;

when the wind power does not exceed the preset overload limit value, the braking system 20 is in a non-braking state; at this time, the locking end 505 of the V-shaped transmission member 502 hooks the locking mating end 606 of the locking unlocking member 603, so that the linkage locking end 607 of the locking unlocking member 603 is separated from the ratchet groove 609 of the locking ratchet 601; this allows no linkage between the brake ratchet 601 and the brake gear 602, i.e. the brake gear 602 remains stationary while the brake ratchet 601 follows the brake link 604;

when the sail moves towards the direction close to the transmission return spring 404 along with the increase of wind power, the sail drives the free slide block 403 to move towards the direction close to the transmission return spring 404 through the free connecting rod 401, the transmission return spring 404 is continuously compressed, and the stepped guide groove 405 also continuously moves, so that the position of the third ball head 504 in the stepped guide groove 405 is also continuously changed; of course, in this process, the locking latching end 505 of the V-shaped transmission member 502 still hooks the latching mating end 606 of the locking releasing member 603, so that the linkage latching end 607 of the locking releasing member 603 is kept separated from the ratchet groove 609 of the locking ratchet 601;

when the wind increases beyond the overload limit, the braking system 20 enters a braking state from a non-braking state; the specific process is as follows: with the increase of wind power, the sail further drives the free slide block 403 to move towards the direction close to the transmission return spring 404 through the free connecting rod 401 under the action of the wind power; in the process, the transmission return spring 404 is further compressed, and one end of the stepped guide groove 405 far from the transmission return spring 404 further moves towards the direction close to the third ball head 504, and finally the third ball head 504 abuts against one end of the stepped guide groove 405 far from the transmission return spring 404; it should be noted that, in the process, the V-shaped transmission member 502 rotates along the support link 501 by an angle, and the locking end 505 of the V-shaped transmission member 502 is separated from the locking end 606 of the locking and unlocking member 603;

after the brake locking end 505 is separated from the locking end 606, the brake unlocking piece 603 is linked with the locking end 607 to approach the brake ratchet 601 under the elastic action of the limiting elastic sheet 605 and finally locked with the ratchet groove 609 of the brake ratchet 601; after the braking unlocking piece 603 is locked with the braking ratchet 601, linkage is formed between the braking gear 602 and the braking ratchet 601; this causes the brake ratchet 601 to rotate with the brake link 604, which drives the brake gear 602 to rotate; when the brake gear 602 rotates, the transmission gear 100 is driven to rotate, so that the swing brake type speed reducer 10 is driven to operate, and the speed of the transmission shaft is reduced; the phenomenon that the wind power generator runs in an overload mode due to the fact that the rotating speed of a transmission shaft is too high due to too large wind power is avoided;

the swing brake type braking system 20 of the wind driven generator decelerates a transmission shaft of the wind driven generator when wind power is too large; the phenomenon that the wind power generator runs in an overload mode due to the fact that the rotating speed of a transmission shaft is too high due to too large wind power is avoided; moreover, the braking system 20 of the invention can sense the magnitude of the wind power in real time, and instantly enters a braking state to perform deceleration processing when the wind power exceeds a preset overload limit value, so that the braking is rapid and timely while automatic braking is realized;

when the wind power decreases below a preset overload limit value, the braking system 20 returns to a non-braking state and no longer brakes the wind turbine; the specific process is as follows: when the wind power is reduced, the wind power borne by the sail is reduced; at this time, the free slide 403 is reset in a direction away from the transmission return spring 404 under the elastic force of the transmission return spring 404; at this time, one end of the stepped guide slot 405 close to the transmission return spring 404 reaches the third ball head 504 of the displacement sensing end 503 and is matched with the third ball head 504; at this time, the V-shaped transmission member 502 is rotated and reset, and the braking locking end 505 of the V-shaped transmission member 502 hooks the locking end 606 of the braking unlocking member 603 again, so that the linkage locking end 607 of the braking unlocking member 603 is separated from the ratchet groove 609 of the braking ratchet 601;

the swing brake type braking system 20 of the wind driven generator can be instantly switched from a braking state to a non-braking state when the wind power is reduced from exceeding a preset overload limit value to being lower than the preset overload limit value, so that the wind driven generator can generate power stably and continuously in real time;

moreover, the swing braking type braking system 20 of the wind driven generator can be repeatedly switched between a braking state and a non-braking state according to the size of wind power when the wind speed is repeatedly shifted near a preset overload limit value; therefore, the wind driven generator is reliably protected in real time.

The above-mentioned embodiments only express several embodiments of the present invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the invention. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the inventive concept, which falls within the scope of the present invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.