EP3450099A1 - Floor grinding machine for grinding and polishing floors - Google Patents

Abstract

The floor grinding machine (1) according to the invention for grinding and polishing floors comprises a chassis (30), a guide tongue (22) and a support structure (20) for supporting a drive motor (2). The drive motor (2) is designed as an electric motor with a rated motor speed of at least 4000 min -1. Furthermore, a rotary grinding tool (24) for rotating grinding or polishing of the bottom and a reduction gear (3, 9) are provided, wherein the reduction gear (3, 9) on the drive side with the drive motor (2) is connected. The output (7) of the reduction gear (3, 9) is provided to drive the rotary grinding tool (24).

Description

Technical area

The invention relates to a floor grinder for grinding and polishing floors, such as concrete floors, stone floors or wooden floors.

With a rotary grinding tool suitable for the respective application, the floor grinding machine can be used, for example, to smooth out unevenness on concrete surfaces, to remove shuttering seams, sleeper skins, old coatings, plastic coatings, adhesive residues and joint residues during tile renewal, to roughen smooth surfaces indoors and outdoors or to polish used by stone floors.

State of the art

From the state of the art DE 20 2015 102 921 U1 a floor grinding machine is known, which is used for abrasive processing of soils. The machine has an electric drive, wherein the drive shaft is vertically aligned and is coupled to the sun gear of a planetary gear. The drive shaft and the sun gear rotate at a speed of 1290 min ^-1. The planet gears of the planetary gear turn on a circular path with 142 min ^-1 around the sun wheel. A tool holder plate can via a slow-speed adapter or be coupled via a high-speed adapter to the output of the planetary gear. Depending on requirements, the tool holder plate can now be coupled by means of the corresponding adapter to the output of the planetary gear, that the tool holder ^plate rotates either 1290 min ^-1 or 142 min ^-1 . Thus, the removal of the floor grinding machine is sufficiently large even at a 1290 min ^-1 rotating large tool holder plate (with, for example 300 mm diameter), the motor must provide a correspondingly large torque. This leads constructively to the fact that the floor grinder has a relatively large volume of construction and a relatively high weight. This makes the entire floor grinding machine difficult and unwieldy. These disadvantages are particularly noticeable when the floor grinder is to be lifted by one person, for example, to lift them from or into a vehicle. It may even be necessary for several persons to lift the machine.

A floor grinding machine which can be operated on the 230 V alternating current network is offered by Contec GmbH, Alsdorf, under the name Alpha on the website http://www.contecgmbh.com/product/alpha.html. The corresponding data sheet can be found on the website http://www.contecgmbh.com/fileadmin/Produkte/Oberflächentechnik/ALPHA/9_01.pdf. This floor sander has a weight of 44 kg according to the manufacturer. Thus, the machine may be too heavy to be lifted by a single person or into a vehicle. According to the data sheet, the grinder derives a nominal current IN = 13 A from the 230 V AC grid and has a power of P = 2 kW and a tool speed from 1290 min ^-1 . Assuming that the power of 2kW is the mechanical power output from the motor, there will be a torque M on the motor shaft and tool receiving plate (diameter 230mm) of: $$M=\frac{\mathrm{<figure-callout\; id="2"\; label="P"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">P</figure-callout>}}{2\pi \cdot N}=\frac{2000\mathit{<figure-callout\; id="2"\; label="W"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">W</figure-callout>}}{2\pi \cdot 1290{\mathit{min}}^{-1}}=14.\mathrm{8th}\mathit{nm}$$

This in turn results in a ratio of torque to machine weight of 14.8 Nm / 44 kg = 0.33 Nm / kg.

Presentation of the invention

An object of the invention is to provide a floor grinding machine for grinding and polishing floors, which is light, compact and easy to transport.

Advantageously, the floor grinding machine according to the invention has a significantly lower weight and smaller dimensions compared to performance-comparable floor grinding machines.

In addition, the inventive floor grinding machine advantageously has a significantly higher ratio of torque to machine weight than the grinding machine according to the prior art.

The object is achieved by a floor grinder for grinding and polishing floors with the features specified in claim 1.

The floor grinding machine according to the invention for grinding and polishing floors comprises a chassis, a guide tongue and a support structure for supporting a drive motor. The drive motor is designed as an electric motor with a rated motor speed of at least 4000 min ^-1 and preferably of at least 6000 min ^-1 . Furthermore, a rotary grinding tool for rotating grinding or polishing of the bottom and a reduction gear are provided, wherein the reduction gear is drivingly connected to the drive motor. The output of the reduction gear is provided to drive the rotary grinding tool.

It can be provided that the drive motor is designed as an electric motor with a rated motor speed of 22000 min ^-1 and.

Advantageous developments of the invention will become apparent from the features indicated in the dependent claims.

In one embodiment of the inventive floor grinding machine, the drive motor is designed as a single-phase AC motor. The advantage of the single-phase AC motor is that it can be operated with alternating current, which is more commonly available than three-phase or direct current.

In another embodiment of the inventive floor grinding machine, the drive motor is designed as a brushed motor. Brushed motors are inexpensive to produce.

In a further embodiment of the inventive floor grinding machine, the drive motor is designed as a brushless or electronically commutated motor. Brushless motors are low-maintenance or even completely maintenance-free.

Advantageously, in the inventive floor grinding machine, the motor shaft of the drive motor is arranged horizontally. As a result, the motor can be built elongated with a small diameter, without its dimensions increase the dimensions of the floor grinder. The construction volume of the floor grinding machine is optimally utilized.

In a development of the inventive floor grinding machine, a frequency converter is provided with which the drive motor can be operated at a frequency of at least 400 Hz.

In an additional development of the inventive floor grinding machine, the reduction gear is designed so that it reduces the rated speed at the output to not less than 1800 min-1. With a rated speed of 1800 min ^-1 or higher, a particularly high stock removal (cut meter output) is achieved.

In another development of the inventive floor grinding machine, the reduction gear has an angle gear, wherein the output shaft is vertically aligned. Angular gear can be produced inexpensively. In addition, the vertically oriented output shaft of the angle gear can easily to another Gear, for example, a traction mechanism can be coupled.

Alternatively, the reduction gear in the inventive floor grinding machine may have a spur gear, which adjoins the drive motor, wherein the motor shaft of the drive motor and the output shaft of the spur gear are arranged vertically.

In the inventive floor grinding machine can also be provided that the reduction gear has a gear transmission and a traction mechanism. One advantage of having a traction mechanism follow the gear transmission is, inter alia, that the traction mechanism can act as overload protection. If the rotary grinding tool blocked, for example, the traction means can slip on one of the deflection pulleys of the traction mechanism. This not only the drive motor, but also the gear transmission can be protected.

In the inventive floor grinding machine, the traction means may be formed as a flat belt or as a toothed belt.

In the inventive floor grinding machine advantageously a fan for ventilating the drive motor is provided. Thus, the heat generated by the drive motor waste heat can be removed.

In addition, it can be provided in the inventive floor grinding machine that the rotary grinding tool has a grinding cup or a grinding plate with a diameter between 250 and 350 mm. With such a large rotary grinding tool can be processed in a short time a large area.

Finally, in the case of the floor grinding machine according to the invention, a quick-release device can be provided for fastening the rotary grinding tool.

Brief description of the drawings

Figur 1

zeigt eine mögliche Ausführungsform der erfindungsgemässen Bodenschleifmaschine in einer dreidimensionalen Ansicht.

Figur 2

zeigt die erfindungsgemässe Bodenschleifmaschine von hinten.

Figur 3

zeigt die erfindungsgemässe Bodenschleifmaschine in der Seitenansicht.

Figur 4

zeigt die erfindungsgemässe Bodenschleifmaschine in der Draufsicht.

Figur 5

zeigt die erfindungsgemässe Bodenschleifmaschine von unten.

Figur 6

zeigt die Antriebseinheit der erfindungsgemässen Bodenschleifmaschine in der Seitenansicht.

Figur 7

zeigt die Antriebseinheit der erfindungsgemässen Bodenschleifmaschine von hinten.

Figur 8

zeigt die Antriebseinheit der erfindungsgemässen Bodenschleifmaschine in der Draufsicht.

In the following, the invention will be explained in more detail with reference to eight figures.

FIG. 1

shows a possible embodiment of the inventive floor grinding machine in a three-dimensional view.

FIG. 2

shows the inventive floor grinding machine from behind.

FIG. 3

shows the inventive floor grinding machine in side view.

FIG. 4

shows the inventive floor grinding machine in plan view.

FIG. 5

shows the inventive bottom grinding machine from below.

FIG. 6

shows the drive unit of the inventive floor grinding machine in side view.

FIG. 7

shows the drive unit of the inventive floor grinding machine from behind.

FIG. 8

shows the drive unit of the inventive floor grinding machine in plan view.

Ways to carry out the invention

In the FIGS. 1 to 5 is a possible embodiment of the inventive floor grinding machine 1 shown in different views. For a better illustration of the construction of the floor grinding machine 1, the machine hood or short hood 11, in the FIGS. 1 to 5 shown next to the machine 1.

The floor grinding machine 1 comprises a chassis 30, which may have, for example, a first wheel 17 and a second wheel 18 and an axle 19. If necessary, the chassis 30 may also have one or more further, not shown in the figures wheels. The two wheels 17 and 18 are connected to each other via the axis 19 and rotatably supported on the axis 19.

The floor grinding machine 1 also comprises a support structure 20 for supporting an electric drive 2. The support structure 20 may be fastened to the axle 19.

For steering, guiding and controlling the floor grinding machine 1, the machine has a guide bar or in short Drawbar 22 with a handle 23. With the help of the drawbar 22, the operator can perform the floor grinder 1 on the ground to be processed by pushing the machine in front of him or pulls behind him. For example, the drawbar 22 may be attached to the axle 19 or to the support structure 20.

In order to tilt the floor grinding machine 1 forward or backward, that is, to be able to rotate about the axis 19, a bracket 28 may be attached to the axle 19. The bracket 28 serves as a tipping aid. In order to tilt the floor grinder 1 easily, the operator can climb with one foot on the bracket 28 and at the same time press the handle 23 down with his hands. In this way, the front part of the floor grinding machine 1, which inter alia includes the drive motor 2 and a rotary grinding tool 24, can be raised. In this state, the chassis 30 serves to make the floor grinding machine 1 easily maneuverable by the operator.

The handle 23 may include controls such as an on / off switch, an emergency stop switch, and a speed controller for controlling the drive 2.

The drawbar 22 may have a rear rod 22.2 and a front rod 22.3 and between them a lockable joint 22.1. When the hinge 22.1 is unlocked, the rear bar 22.2 of the drawbar 22 together with the handle 23 can be pivoted forward onto the front bar 22.3. The hinge 22.1 may be configured to automatically lock when the rear rod 22.2 projects forward on the front rod 22.3 was panned. By pivoting the rear rod 22.2 forward, the entire floor grinding machine 1 becomes more compact and handy. This is particularly advantageous for the transport of the floor grinding machine 1.

Between the front rod 22.3 and the rod 22.5, another joint 22.4 may be provided so that the front rod 22.3 can still be pivoted forward. However, it is also possible to design the further joint 22.4 such that the front rod 22.3 can be pivoted downwards to the two wheels 17 and 18. With both variants, the floor grinding machine 1 becomes even more compact and handy. The joint 22.4 can also be designed as an automatically locking joint.

In the front part of the floor grinding machine 1, at the bottom on the side facing the soil to be processed, there is the rotary grinding tool 24, which may have different abrasives. The rotary grinding tool 24 may include, for example, a cup wheel with a series of abrasive segments 25. The rotary grinding tool 24 may also include a sanding pad having a series of abrasive segments 25. Opposite the cup, the sanding plate is flat or flatter. The abrasive segments 25 may include, for example, diamonds and be releasably attached to the cup or on the grinding plate or attached. The abrasive segments 25 may be screwed, welded or soldered, for example, on the cup wheel or on the sanding pad.

Advantageously, the floor grinding machine 1 has a quick-release device 26 with which the rotary grinding tool 24 can be fastened to the output shaft 7 of the reduction gear 9. As a result, the rotary grinding tool 24 can be replaced by the operating personnel quickly and easily.

The floor grinding machine 1 may have a suction hood 12, which surrounds the rotary grinding tool 24 and also serves as protection. The suction hood 12 may have one or more suction nozzles 13, 14 to which hoses, not shown in the figures, can be connected. The hoses can be brought together via a arranged on the drawbar 22, y-shaped hose holder. From there, the dust produced during grinding or polishing can be passed via a further hose to a suction station, not shown in the figures. The suction station may be, for example, an industrial vacuum cleaner.

The electric drive motor 2 and the reduction gear 9 of the floor grinding machine 1 are in the FIGS. 6, 7 and 8 shown.

As electric drive motor 2 is an electric motor with a rated speed N _Mot of at least 4000 min ^-1 and even better with a rated speed of at least 6000 min ^-1 . In a preferred embodiment, the nominal speed N _mot of the motor 22000 min ^-1. Such a high speed rotating electric motor can be built very easily and comes with an exceptionally small volume.

Preferably, the electric motor is designed as a brushless or brushed single-phase AC motor.

The electric motor 2 can also be a three-phase motor, provided that it can provide the above-mentioned speed N _Mot . As a three-phase current is understood here the combination of three alternating currents of the same frequency, which are shifted from each other in their phase angles by 120 °. The three-phase motor is preferably operated with a frequency converter which can be connected to the single-phase AC mains. This has the advantage that the network side no three-phase network is required, but only a single-phase AC power sufficient to operate the engine can.

The single-phase AC motor, hereafter referred to as AC motor, does not require a three-phase power supply as compared to the AC motor. As a result, the flexibility of the floor grinding machine 1 equipped with an AC motor increases with respect to the place of use because alternating current is more available than three-phase current.

The AC motor may be formed, for example, as a single-phase series motor. This motor can generate the required rated speed N _Mot in a small space. It also provides a sufficiently high starting torque. If necessary, the speed and the power can be adjusted via an electronic control, such as a phase control or even regulated if necessary.

It is also conceivable to design the electric drive motor 2 as an asynchronous motor and to operate it with an electronic frequency converter on the AC mains. The frequency converter initially rectifies the single-phase AC voltage and then electronically converts the DC voltage thus generated into a three-phase alternating voltage with a rotating field of frequency f. With the aid of the frequency converter, the engine speed can be set via the frequency f. In addition, if required, the torque provided by the drive motor 2 can also be specified with the aid of the frequency converter.

For example, the frequency converter can produce a rotating field with a frequency f of 400 Hz at which the motor is operated.

Alternatively, can serve as a drive motor 2, a brushless DC motor, which can be operated with an electronic converter feed in the AC network.

If necessary, the drive motor 2 can be equipped with a fan 15 in order to be able to better carry away the heat generated by it during operation. If necessary, a further fan can be provided. For example, one of the two fans may be arranged at the rear near the axis 19 and the other fan at the front end of the drive motor 2.

The reduction gear 9 of the floor grinding machine 1 is used to reduce the engine speed N _Mot to an idle speed or in short rotational speed N2, which is suitable for the respective rotary tool. The speed N2 is hereinafter also referred to as output speed N2 of the reduction gear 9 and the speed of the output shaft 7 reduction gear. 9

In the in the FIGS. 6-8 In the embodiment shown, the reduction gear 9 comprises an angle gear 3 and a traction mechanism 9. The angle gear 3 is connected to the drive shaft of the drive motor 2 on the drive side. On the output side, the angle gear 3 has a gear outlet 6, which carries a pulley 5, which is part of the traction mechanism 9. Thus, the angle gear 3 is coupled on the output side with the traction mechanism 9 and generates at the gear outlet 6 a speed N1. The traction mechanism 9 in turn is the output side connected to the rotary grinding tool 24 and generates the speed N2.

The ratio i1 of the angular gear 6 is: $$i1=\frac{{\mathrm{<figure-callout\; id="1"\; label="N\; Mot\; N"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">N\; </figure-callout>}}_{\mathit{Mot}}}{N}$$

The ratio i2 of the traction mechanism 9 is: $$i2=\frac{N1}{\mathrm{<figure-callout\; id="2"\; label="N"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">N</figure-callout>}2}$$

The speed N2 is thus calculated as follows: $$\mathrm{<figure-callout\; id="2"\; label="N"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">N</figure-callout>}2=\frac{{\mathrm{<figure-callout\; id="1"\; label="N\; Mot\; i"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">N\; </figure-callout>}}_{\mathit{Mot}}}{i}$$

For example, if the rated speed of the drive motor N _Mot = 22000 min ^-1 , the ratio of the angular gear i1 = 3.3 and the translation of the traction mechanism i2 = 2.5, results for the speed N2 at the output 7: $$\mathrm{<figure-callout\; id="2"\; label="N"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">N</figure-callout>}2=\frac{{\mathrm{<figure-callout\; id="1"\; label="N\; Mot\; i"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">N\; </figure-callout>}}_{\mathit{Mot}}}{i}=\frac{22000{\mathit{min}}^{-1}}{3.3\cdot 2.5}\approx 2670{\mathit{min}}^{-1}$$

The torque M ₇ at the output 7 is calculated with the above-mentioned rated engine speed N _Mot and a rated engine power (mechanical power output of the engine) P = 2400 W to: $${\mathrm{<figure-callout\; id="7"\; label="M"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">M</figure-callout>}}_7=\frac{\mathrm{<figure-callout\; id="2"\; label="P"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">P</figure-callout>}}{2\pi \cdot \mathrm{<figure-callout\; id="2"\; label="N"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">N</figure-callout>}2}=\frac{2400\mathit{<figure-callout\; id="2"\; label="W"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">W</figure-callout>}}{2\pi \cdot 2670{\mathit{min}}^{-1}}=\mathrm{8th}.58\mathit{nm}\left(\mathrm{rated\; torque}\right)$$

On the other hand, if the ratio i1 * i2 is chosen such that a speed N2 at the output 7 of N2 = 1290 rpm results, the nominal torque M _{7 is} : $${\mathrm{<figure-callout\; id="7"\; label="M"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">M</figure-callout>}}_7=\frac{\mathrm{<figure-callout\; id="2"\; label="P"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">P</figure-callout>}}{2\pi \cdot \mathrm{<figure-callout\; id="2"\; label="N"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">N</figure-callout>}2}=\frac{2400\mathit{<figure-callout\; id="2"\; label="W"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">W</figure-callout>}}{2\pi \cdot 1290{\mathit{min}}^{-1}}=17.\mathrm{8th}\mathit{nm}\left(\mathrm{rated\; torque}\right)$$

The ratio of torque M ₇ to machine weight results in: $$\frac{{\mathrm{<figure-callout\; id="7"\; label="M"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">M</figure-callout>}}_7}{2\pi \cdot \mathrm{<figure-callout\; id="2"\; label="N"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">N</figure-callout>}2}=\frac{17.\mathrm{<figure-callout\; id="28"\; label="8th\; nm"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">8th\; </figure-callout>}\mathit{nm}\mathit{}}{28\mathit{kg}}=0.64\frac{\mathit{nm}}{\mathit{kg}}$$

The ratio of torque M ₇ to machine weight is thus about twice as large as that of the grinding machine according to the prior art. Since this ratio is also of particular importance for the removal rate of the grinding machine, this results in a considerable improvement (higher removal rate) compared to the prior art. In addition, the inventive grinding machine with a weight of 28 kg is light enough to be raised by a single person or in a vehicle can.

The maximum torque of the drive motor M _MaxMot shortly before standstill is, for example, 5.1 Nm. The torque N _Max7 at the output 7 shortly before the stoppage of the drive motor is then determined to be: $${\mathrm{<figure-callout\; id="7"\; label="M\; Max"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">M\; </figure-callout>}}_{\mathrm{Max}}={\mathrm{M}}_{\mathrm{MaxMot}}*\mathrm{i}\mathrm{1}*\mathrm{<figure-callout\; id="2"\; label="i"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">i</figure-callout>}\mathrm{2}=\mathrm{5}.\mathrm{1}\mathrm{nm}*\mathrm{3}.\mathrm{3}*\mathrm{2}.\mathrm{5}=\mathrm{42}.\mathrm{1}\mathrm{nm}$$

The traction mechanism 9 may be formed, for example, as a belt transmission. One possible embodiment of a belt drive is FIG. 6 shown in the side view. The belt drive comprises the belt pulley 5, a belt 4 and on the output side a belt pulley 8. The transmission i2 of the belt transmission is determined by the diameters of the two pulleys 5 and 8.

Instead of the belt 4, any other traction means such as a chain is conceivable.

When the belt 4 is formed without teeth, the force is non-positively transmitted from the pulley 5 to the pulley 8. The toothless belt can advantageously take over the function of a safety clutch in addition to the power transmission. For example, if the rotary grinding tool 24 is blocked or its frictional resistance is too high a load for the electric motor 2, the belt 4 may slip on the pulley 5 and / or the pulley 8. This not only the electric motor 2, but also the bevel gear 3 are protected.

If, however, the belt 4 is designed as a toothed belt, the power transmission takes place from the pulley 5 the pulley 8 positive fit. With the toothed belt, the expansion slippage occurring in the edentulous belt can be eliminated.

When using the toothed belt, the radial load of the output 6 of the angular gear 3 is lower than when using a toothless belt. The reason for this is that with a toothless belt, the force from the pulley 5 to the belt 4 can only be frictionally transmitted. The toothless belt must therefore be kept under tension more than the toothed belt, which represents a greater radial load for the output 6 than when using the toothed belt. For the life of the angular gear 3, it may be advantageous if the radial load at the output 6 is low.

In order to tension the toothless belt, a tensioning device is advantageously provided, which presses on a single, not on the pulleys 5 and 6, the free belt section, which is also referred to below as Trum. The tensioning device can press on the tensioned free belt section (Lasttrum) or on the pulled strand (empty strand).

The axis of rotation 21 of the drive shaft of the electric drive motor 2 is in the in FIGS. 6 to 8 embodiment shown aligned horizontally. The axis of rotation 61 of the output 6 is aligned vertically and extends parallel to the axis of rotation 71 of the output shaft. 7

The foregoing description of the embodiments according to the present invention is for illustrative purposes only, and not for the purpose of limiting the invention. Various changes and modifications are possible within the scope of the invention. For example, in the FIGS. 1 to 8 shown components of the floor grinding machine can also be combined with each other in a different manner as shown in the figures. For example, the angle gear 3 can be replaced by a spur gear.

If instead of the angular gear 3, a spur gear is used, the axis of rotation 21 of the drive motor 2 is preferably vertical. The output shaft of the spur gear is parallel to the axis of rotation 21 and thus also vertically. On the output shaft of the spur gear, the above-described Zugsmittelgetriebe 9 may be coupled. Thus, in this embodiment, the axis of rotation of the drive motor 2 and the axes of rotation of the spur gear and the axes of rotation of the Zugsmittelgetriebes 9 parallel to each other.

The engine hood 11 is intended to cover the reduction gear 9 in order to protect persons from injury. The machine hood 11 can also be provided to cover the drive motor 2, so that it is secured against impacts and bumps.

To fix the machine hood 11 on the support structure 20, for example, one or more holes 11.1, 11.2 and 11.3 may be provided in the hood 11. Through these holes screws can be plugged and these then screwed into one or more threaded holes 20.1, 20.2, which are provided for this purpose in the support structure 20. The hood 11 may have corresponding ventilation slots 11.4 for better removal of heat.

As in the FIGS. 1 to 4 For example, the supporting structure 20 may be formed as a housing for covering the angular gear 3 and a part of the traction mechanism 9.

For holding the drive motor 2, a separate motor mount 10 may be provided. The motor mount 10 may also be part of the support structure 20.

LIST OF REFERENCE NUMBERS

1

floor grinder

2

drive motor

3

angle gear

4

belt

5

pulley

6

transmission output

7

Output shaft / output

8th

pulley

9

traction drives

10

engine mount

11

engine hood

11.1

mounting hole

11.2

mounting hole

11.3

mounting hole

11.4

vents

12

exhaust hood

13

suction

14

suction

15

Fan

17

wheel

18

wheel

19

axis

20

supporting structure

21

Rotary axis of the motor shaft

22

steering arm

22.1

joint

22.2

rear bar

22.3

front bar

22.4

joint

22.5

pole

23

Handle

24

Rotary grinding tool

25

abrasive segment

26

Quick clamping device

28

hanger

29

hose holder

30

chassis

61

Rotation axis of the output

71

Rotation axis of the output

Claims (15)

Floor grinding machine for grinding and polishing floors, - In which a chassis (30), a guide tongue (22) and a chassis (30) fixed support structure (20) for supporting an electric drive motor (2) are provided, - in which the drive motor (2) has a rated engine speed of at least 4000 min ^-1, - In which a rotary grinding tool (24) is provided for rotating grinding or polishing of the soil, and - In which a reduction gear (3, 9) is provided, the drive side is connected to the drive motor (2) and the output (7) of the reduction gear (3, 9) is provided to drive the rotary grinding tool (24). Floor grinding machine according to claim 1,
in which the drive motor (2) is designed as a single-phase AC motor. Floor grinding machine according to one of the preceding claims,
in which the drive motor (2) is designed as a brushed motor. Floor grinding machine according to one of the preceding claims 1 or 2,
in which the drive motor (2) is designed as a brushless motor. Floor grinding machine according to one of the preceding claims,
in which the motor shaft of the drive motor (2) is arranged horizontally. Floor grinding machine according to one of the preceding claims,
in which a frequency converter is provided, with which the drive motor (2) is operable at a defined frequency. Floor grinding machine according to one of the preceding claims,
wherein the reduction gear (3, 9) is designed such that the idle speed (N2) at the output (7) is at least 1800 min ^-1 . Floor grinding machine according to one of the preceding claims,
in which the reduction gear (3, 9) has an angular gear (3). Floor grinding machine according to one of the claims 1 to 4 or 6 to 8, - In which the reduction gear (3) has a spur gear, and - In which the motor shaft of the drive motor (2) is arranged vertically. Floor grinding machine according to one of the preceding claims,
in which the reduction gear (3) has a gear transmission. Floor grinding machine according to one of the preceding claims,
in which the reduction gear (3) has a traction mechanism (9). Floor grinding machine according to claim 11,
in which the traction means of the traction mechanism (9) as a flat belt or as a toothed belt (4) is formed. Floor grinding machine according to one of the preceding claims,
in which a fan (15) is provided for ventilating the drive motor (2). Floor grinding machine according to one of the preceding claims,
in which the rotary grinding tool (24) has a grinding cup or a grinding disc with a diameter of at least 250 mm. Floor grinding machine according to one of the preceding claims,
in which a quick-release device (26) is provided for fastening the rotary grinding tool (24).

Images