RU14828U1 - TIP DENTAL TURBINE FRICTION (OPTIONS) - Google Patents

Description

The proposed technical solution relates to medical equipment, namely to mechanized dental instruments and can be used to fix rod tools in turbine tips.

There is a Clause for the Tool Clamp (application FRG 14 033846248, IPC A 61 C 1/14, B 23 B 31/04, Inventions of the world, issue N 13, bulletin N S, 1986.

The clamp for dental instruments contains a sleeve mounted in the tip connected to a rotary drive. The sleeve is equipped with spade elements and a spring. Elements act on the tool shank installed in the receiving sleeve inward, in the radial direction. The clamp is provided with a spring, and the clamping elements contain at least one clamping jaw, forming a separate node relative to the receiving sleeve.

Due to the miniature size of the head, this design is used in turbine applications due to the complexity and bulkiness of the structure.

300 - 05, manufactured at the enterprises of GUL NLP Mikron, Kazan, OJSC Metalist Serpukhov, OJSC Arzamass Instrument-Making Plant, etc.

By design, the tip is a hollow roller with a turbine mounted in two ball bearings in damping bearings, which are rubber rings. One of the bearings on the damping ring is installed in the housing grommet, and the other in the housing bore and spring-loaded through the cage. On the roller, there are two reciprocal grooves against each other, in which the liners, which are spring plates, are laid. The aluminum alloys D16 and B95 are used as the tourbium material; similar aluminum alloys are used for these purposes in foreign designs. The main disadvantage of frictional turbine dental tips is the change in the boron retention force during operation. This is due to the fact that the contribution by design features cannot be more than 2.6 mm in length. The liner is about 0.60.8 mm thick, and for effective retention it undergoes a bend of about 0.15 mm. The tip in accordance with the technical conditions must withstand at least 2000 cycles of insertion - removal of the cutting tool, not exceeding the limits of the insertion - extraction force from 4. to E kg. The NTO - 300 - 05 tips do not withstand these requirements.

In addition, turbine tips in accordance with the technical conditions must have an MTBF of at least ISO hours. The main reason for the failure of the tip is the breakdown of the ball bearings. This is because of that. that the roller with the impeller idling rotates in ball bearings with a frequency of over 300,000 rpm, and the ball bearings cannot withstand loads. The main load on the ball bearing is the unbalance of the turbine. Foreign manufacturers produce static and dynamic balancing of the turbine. Domestic manufacturers do not do balancing due to the high price of equipment for balancing and the complexity of this process.

At present; its time, the damping rings of the turbine tips are made of oil - petrol-resistant rubber based on nitrile rubbers N 3826 TU 0051166 with a working temperature limit of +. It is known that after applying a turbine tip, it must be sterilized in order not to infect the next patient with various types of infectious diseases. Sterilization is carried out in an autoclave at a pressure of kg / cj / and a temperature of 134 ° C for at least 20 minutes. With repeated exposure to temperature, rubber damping rings from rubber mixtures of type N 3826 become rigid and do not fulfill their purpose - damping of alternating loads on ball bearings.

As a result, ball bearings fail faster, noise from the turbine is increasing.

The technical problem to be solved in the proposed technical solution is to increase the reliability of the tip.

The technical problem to be solved is in the dental friction friction tip, its first variant, comprising a housing with a connection unit with a drill hose and a head with a cover, spring inserts installed in the head on a roller having a cylindrical inner cavity, a turbine located on the roller in ball bearings with damping shea rings, is achieved by the fact that in the roller there are at least two radial through grooves located along the axis of the roller, and the liners are made curved along a radius corresponding to the radius through grooves on the roller, damping rings are made of rubber based on fluororubber with a hardness of Shore A - 65 - 80, and the turbine is made of carbon-filled polyamide with a density of 1.2 1.4 g / cm, carbon fiber mass fractions from SO to 50 percent.

The technical problem to be solved is in the dental friction friction tip, its second variant, comprising a housing with a unit. Connections with a drill hose and a head with a cover, spring inserts installed in the head on a roller having a cylindrical internal cavity, a turbine located on the roller in damping ball bearings rings, is achieved by the fact that at least two radial through grooves are made in the roller, located along the axis of the roller, and the liners are made curved along the radius corresponding to the radius have through slots on the platen.

The technical problem to be solved is in the dental friction friction tip, its third variant, comprising a housing with a connection unit with a drill hose and a head with a cover, spring inserts installed in the head on the roller, having a cylindrical internal cavity, a turbine located on the roller in ball bearings with damping rings , is achieved by the fact that the damping rings are made of rubber based on fluororubber with a hardness in units of Shore A - 65 .... 80.

The technical problem to be solved is in the dental friction friction tip, its fourth variant, comprising a housing with a connection unit with a drill hose and a head with a screw, spring inserts installed in the head on the roller, having a cylindrical internal cavity, a turbine located on the roller in ball bearings with damping shea rings, is achieved by the fact that the impeller is made of carbon-filled polyamide with a density of 1.2 g / 1.4 g / cm, mass fraction of carbon fiber from EO to 50 percent.

For example, carbon-filled polyamides of the UPA-66 type according to TU - 12 - 31 - 833 - 95 can be used. Carbon-filled polyamides of the UPA-66 type. Technical specifications. The most applicable are UPA - 66 - 20, UPA 66 - 30 and UPA - 66 - 40. Carbon-filled polyamide 6 - Armamide PA UV-30 can be used. Fluororubber-based rubber for the third version of the proposed technical solution can be used fluoride rubber according to TU 0051166 - 87 Rubber compounds for parts of aircraft. - Technical conditions. As the main ones, heat-frost-oil-resistant rubber based on fluorosiloxane rubbers can be used, for example, 51-1434 and 51-1570. Heat-resistant rubber based on fluororubbers or, for example, IRP 1313 according to TU 38105 1082 - 86 can be used. , gr. 111 - 38 - 12.

In FIG. 1 shows the tip of the dental turbine frictional friction general view, its first, second, third and fourth options.

In FIG. 2 shows a longitudinal section of the tip head, figuratively.

In FIG. 3 shows a cross section along the roller, enlarged.

In FIG. 4 shows a longitudinal section of the roller along the liners, enlarged.

In FIG. 5 shows the insert, enlarged.

Dental turbine tip With FIG. 1-5) its first embodiment, comprises a housing 1 with a connection unit with a drill hose S and a head 3 with a cover 4, spring inserts 5 mounted in the head 3 on the roller 6 having a slotted inner cavity 7, a turbine 8 located on the roller 6 in ball bearings 9 and 10 with damping rings 11 and 12. At least 6 radial through grooves 13 are made on the roller 6, located along the axis of the roller 6. The liners 5 are made curved along a radius r corresponding to the radius R of the through grooves 13 on the roller 6. Damping rings 11 and 1 are made of rubber on os ove ftorkauchu1yuv with a hardness in terms of Shore A 65 to 80 and the impeller 8 is made of polyamide uglenapolnennogo a density of 1.2 1.4 g / cm, the mass fraction of carbon fibers of 20 to 50 percent. On the cover 4 there is an opening 14 for pushing out boron.

Dental turbine tip (Fig. 1-5), its second variant, comprises a housing 1 with a connection unit with a drill hose and a head 3 with a cover 4, spring inserts 5 installed in the head 3 on a roller 6 having a cylindrical internal cavity 7, a turbine 8, located on the roller 6 in ball bearings 9 and 10 with damping rings 11

And IS. At least two radial through grooves 13 are arranged on the roller 6, located along the axis of the roller 6. The 5 inserts are made curved along the radius r to the corresponding radius R of the through grooves 13 on the roller 6.

Dental turbine tip (Fig. 1-5), its third variant, comprises a housing 1 with a connection unit with a drill hose E and a head 3 with a cover 4, spring inserts 1 and 5 installed in the head 3 on a roller 6 having a cylindrical internal cavity 7, a turbine 8 located on the roller 6 in ball bearings 9 and 10 with damping rings 11 and 12. The damping rings 11 and IE are made of rubber based on fluororubber with a hardness in Shore A units of 65 to 80.

Dental turbine tip (Figs. 1-5), its fourth variant, comprises a housing 1 with a connection unit with a drill hose 2 and a head 3 with a cover 4, spring inserts 5 installed in the head 3 on the roller 6, and a cylindrical inner cavity 7, a turbine 8 located on the roller 6 in ball bearings 9 and 10 with damping rings 11 and IE. The turbine 8 is made of carbon-filled polyamide with a density of 1.2 to 1.4 g / cm and a mass fraction of carbon fiber of 20 to 50 percent.

The proposed tip, according to the first embodiment, works as follows.

A cylindrical shank of a cutting (boron) or grinding (diamond head) core tool is inserted into the internal cavity 7. It moves to the exit point of insert 5 into the internal cavity 7 through the radius through

grooves 13. The shank of the core tool extends the liners 5 and enters the roller 6 over the entire length of the inner cavity 7. In this case, the spring liners 5 are elastically deformed, abutting against the inner surfaces of the ball bearings 9 and 10, holding the cylindrical shank of the core tool. The extraction force of the tool is S4 kgf, while

the diameter of the elastic liners ... d is from 0.5 to 0.9 mm, depending on its length and bending radius g. If it is necessary to remove the core tool, a rod of a special pusher is inserted into the hole 14 on the cover 4 and axial force is applied to it. The pusher rod extends into the internal cavity 7 of the roller 6 and pushes the shank of the core tool. The liners 5 are in their original position. In principle, the design can be operable with one lug 5, but given that this will introduce a large unbalance at a high rotation speed of the turbine 8 (E50 ..... 400 thousand rpm), the minimum possible number of inserts 5 should be at least two. The most rational is the number of inserts 5 equal to three, since in this case the core tool is centered on three points, but 45 inserts 5 are possible, which somewhat complicates the design, but increases reliability.

The width of the groove 13 should be 0.05..0.1 mm wider

the diameter d of the insert 5. The radius R of the through groove 13 on the roller 6 should be equal to the radius r of the bend of the insert 5 or less, up to SO percent. In this case, the output of the bend of the liner 5 into the inner cavity 7 of the roller b will be optimal.

the neck 5 increases their length to almost a length slightly smaller than the roller 6. In this case, the relative deformation (bending) coefficient of the inserts 5 decreases and they will not have permanent deformation, which reduces the retention force of the shank of the core tool. The number of insertion cycles - extraction of the core tool will increase dramatically

almost 3 times and this stability will be ensured

parameter during the entire period of operation of the tip.

When air is supplied to turbine 8 in a short period of time, it develops an idle speed of over 300,000 rpm. At such high speeds, intensive wear of ball bearings 9 and 10 occurs, which is more dependent on the imbalance of the turbine 8. Moreover, the damping rings 11 and IS can reduce the radial load on the ball bearings 9 and 10 from the imbalance of the turbine 8 and disturbances from the one installed in the roller 6 core tool. The damping rings 11 and 12 do not only need to reduce the radial loads on ball bearings 9 and 10 from the imbalance of the turbine 8 and the core tool, but also withstand the loads that arise when cutting (grinding) tooth tissue, which through the cutting tool, inserts 5 and roller 6 transferred to ball bearings 9 and 10. In addition, the turbine tips must be sterilized after each patient with

o3

temperature 134 C, pressure E kgf / cm during SO minutes and it is imperative to be oil resistant at this temperature. Given the need for sterilization, damping and withstanding axial and radial loads applied to the cutting tool, the most optimal material for the manufacture of damping

rings 11 and IS are fluororubber-based rubbers with a hardness in Shore A units of 65 to 80. At a hardness of less than 65, in Shore A units, the rubber compound is too soft, the damping rings 11, IE are too deformed, and large rotor group displacements result when axial and radial loads on a cutting or grinding rod tool. This creates inconvenience and can lead to undesirable contact of the turbine 8 with the inner surface of the head 3, which will lead to breakage of the tip. When the cBbmie rubber compound has a hardness of 80 Shore A units, the damping properties of rings 11 and 12 are insufficient, the load on ball bearings increases, and the noise level during tip operation increases.

All of these conditions correspond to fluorine rubbers according to TU 0051166 - 87, for example, heat - oil-resistant rubbers based on fluorosilaxane rubbers, for example, 51 - 1434 and 51 - 1570 Р1ЛI heat-resistant rubbers based on fluororesins, for example, IRP 1313.

The wear of ball bearings 9 and 10 to a large extent also depends on the imbalance of the turbine 8. To reduce the unbalance of the turbine, static and dynamic balancing is performed. However, if we make turbine 8 from a material of reduced density with the same geometric dimensions and with the same accuracy, then the imbalance will decrease in proportion to the decrease in the density of the material. For example, you can use magnesium alloys with a density of 1.4 r / ci / to 1.9 g / cm, having a sufficiently high strength.

strength. The carbon-filled polyamides UPA - 66 - 20, UPA - 66 - 30 and UPA - 66 - 40, having a density of 1, Е Г / С1 / ДО 1.4 g / ci / s carbon fiber mass fraction from 20 to 50, correspond to these qualities percent. The density of the turbine blades 8 of these materials at linear speeds of more than 150 m / s. - quite sufficient. (Breaking stress at bending 110 ... 140 MPA). When the density of the material of the turbine 8 is 1.2 1.4 g / cm, the imbalance of the turbine B, ceteris paribus, compared with aluminum alloys D16 and B95 having a density of 2.8 g / cm, decreases by more than 2 times. This virtually eliminates the need for balancing the turbine 8 and increases the service life of ball bearings 9 and 10.

Increase the number of insertion / extraction cycles

core tool (23 times), the stability of this

parameter during the entire period of operation, good damping properties of rubber rings, the stability of their parameters at high temperature and pressure in the presence of oils, reduced ball bearing loads of 9.10 due to the damping properties of fluororubber rubbers and reduced imbalance due to the use of carbon-filled polyamides for the manufacture of turbines, allows to significantly increase consumer qualities and reliability of turbine tips.

The tip according to the second embodiment has a design similar to the construction according to the first embodiment, but the manufacture of damping rings 11 and 12 from rubber based on fluororubberies with a hardness in Shore A units of 65 to 80 and the manufacture of a turbine 8 from carbon-filled polyamide with a density of 1.2 1 are excluded 4 g / cm and. mass fraction of carbon fiber

1 g -

FROM 20 to 50 percent. In this case, the reliability of the turbine tips is increased only due to a better and more reliable friction clamp assembly of a cutting or grinding tool C boron or diamond head) compared to existing designs. The description of the work of the proposed design of the tip according to the second embodiment is similar to the description of the operation of the tip according to its first embodiment.

The tip according to the third embodiment has a structure similar to that of the first embodiment, but it has fluff-based rubber damping rings made of rubber with a hardness in Shore units of 65 to 80. In this case, any type of friction or push-button clamp and any turbine material can be used. The reliability of the tip is increased only through the use of rubber damping rings based on fluororubber with a hardness in Shore A units of 65 to 80.

The tip according to the fourth embodiment has only a turbine made of carbon-filled polyamides with a density from 1.2 G / C1G to 1.4 r / ci / K of a mass fraction of carbon fiber from 20 to 50 percent. In this case, the reliability of the turbine tip is increased only by reducing the imbalance of the turbine and the loads on the ball bearings.

Claims (4)

1. The tip of the dental turbine friction, comprising a housing with a connection with a drill hose and a head with a cover, spring liners installed in the head on a roller having a cylindrical internal cavity, a turbine located on the roller in ball bearings with damping rings, characterized in that the roller has made at least two radial through grooves located along the axis of the roller, and the liners are made curved along the radius corresponding to the radius of the through grooves on the roller, damping rings Execute the rubber-based fluoroelastomers having a hardness in units of "Shore A" 65 - 80, and the impeller is made of polyamide uglenapolnennogo a density of 1.2 - 1.4 g / cm ^{3, the} mass fraction of carbon fibers of 20 - 50%.  2. Dental turbine friction tip, comprising a housing with a connection unit with a drill hose and a head with a cover, spring inserts installed in the head on a roller having a cylindrical internal cavity, a turbine located on the roller in ball bearings with damping rings, characterized in that the roller has at least two radial through grooves located along the axis of the roller, and the liners are made curved along the radius corresponding to the radius of the through grooves on the roller.  3. The dental turbine friction tip, comprising a housing with a connection unit with a drill hose and a head, with a cap, spring inserts installed in the head on a roller having a cylindrical internal cavity, a turbine located on the roller in ball bearings with damping rings, characterized in that damping rings are made of rubber based on fluororubber with a hardness in units of Shore A 65 - 80. 4. Dental turbine friction tip, comprising a housing with a connection unit with a drill hose and a head with a cover, spring inserts installed in the head on a roller having a cylindrical internal cavity, a turbine located on the roller in ball bearings with damping rings, characterized in that the turbine made of carbon-filled polyamide with a density of 1.2 - 1.4 g / cm ³ and a mass fraction of carbon fiber of 20 - 50%.