Electric actuator for driving screen used in home environment

FIELD: electricity.

SUBSTANCE: invention relates to an electric actuator for driving a screen. The electric actuator (100) for driving a screen (2) used in a home environment, which moves between its open position and closed position, said actuator being provided with a spring brake (105), said brake having a helical spring (130; 230), each end of which forms a tab (132a, 132b; 232a, 232b) extending radially or axially relative to the central axis (X₁₃₀; X₂₃₀) of the spring; a friction part (140; 240) having a substantially cylindrical friction surface (141; 241) against which at least one turn of the helical spring bears radially; an inlet part (110; 210) driven by the electric motor (103) of the actuator, and configured to come into contact with at least one tab (132a, 132b; 232a, 232b) of the spring, in such a manner as to drive the spring in rotation about the central axis (X₁₀₅) of the brake, in a direction making it possible to reduce the contact force between the helical spring and the friction surface; and an outlet part (120; 220) connected to the screen (2) and configured to come into contact with at least one tab (132a, 132b; 232a, 232b) of the spring in such a manner as to drive the spring in rotation about the central axis (X₁₀₅) of the brake, in a direction making it possible to increase the contact force between the helical spring and the friction surface; wherein, while the screen is being lowered, the inlet part (110; 210) drives the spring (130; 230) in rotation with the contact force being decreased to the extent that the outlet part (120; 220) is released in rotation, without direct contact between the inlet part and the outlet part; wherein the inlet part (110; 210) has at least two contact surfaces (113a, 113d; 213b, 217c) adapted to transmit a drive torque (C_M) for raising the screen (2), by direct contact with at least two corresponding contact surfaces (123a, 123c; 223b, 227a) of the outlet part (120; 220).

EFFECT: design of an electric drive equipped with a spring brake, which improves operation of previous brakes.

10 cl, 11 dwg

The present invention relates to the drive mechanism, designed for the propulsion of the screen used in the home, such as a split flap, blind, curtain, flexible grid, protective screen or garage doors. Drive mechanism in accordance with the invention with a spring brake mechanism. The brake mechanism of this type is preferably adapted for engines of the tubular type.

The use of the brake mechanism with a spiral spring in the drivers designed for use in the home, it is known, in particular from patent document FR-a-2 610 668. According to this patent document, a spiral spring is set in the item of friction. At least one coil spring is in a state of mechanical stress in the radial direction of the through holes made in the details of friction. Each end of the said spring forms a foot, passing in the radial direction inside this spring. Each foot may be moved in such a way as to bring the spring into rotational movement relative to its axis. The input part, the output part and the spring are positioned relative to each other in a special way in order to ensure opisannuyu kinematics, namely, the effect on the input item, settling down with the first foot, brings the spring into rotational movement in the first direction. This movement frees the output item, that is, it seeks to reduce the diameter of the outer envelope of this spring. Thus, the friction between the said hole in the friction and the coils of the spring decreases, which entails a reduction of the radial stress between the spring and the friction detail. Or Vice versa, the impact on the output part, located opposite the first foot, brings the spring into rotational movement in the second direction, i.e. in the direction opposite the first direction. This movement locks the output item, that is, it seeks to increase the diameter of the outer envelope of this spring. Thus, the friction between the said hole in the friction and the coils of the spring increases. The same is the case with radial mechanical stress between the spring and the friction detail. On the other hand, the input item can also act on the second leg of the spring to cause the spring to a rotary motion in said second direction, freeing the output item. At the same time, this output item also has the ability to influence storagepro springs, to bring the spring into rotational movement in said first direction. In this case, the output item is blocked or at least its movement is retarded by friction this spring relative to the details of friction. As a result, the rotation of the input part allows you to provide rotation of the spring and the output part, while the rotation of the output parts leads to the fixing of the spring in a stationary position that blocks movement caused by output item.

Thus, the main braking output part is provided by the friction of the spring relative to the details of friction. And second phenomenon contributes to the braking output details: here we are talking about friction output details at the level of its guide means. This friction is directly related to torque forces applied to the brake. In that case, when the torque of the engine affects the input item, this input item applies force to the output part through the legs of the spring. Because this effort is asymmetric with respect to the axis of the output parts, it leads to radial forces, which causes a shift in the output details up to the position in which she starts to push against his guiding means. This contact leads to inhibition of the output items. In that case the e, when the moment of forces affects the output item, it calls the application of force to the foot of the spring, tending to prevent rotational movement of this spring. In response to this asymmetrical force resulting radial force causes a shift in the output details up to the position in which she starts to push against his guiding means. Thus, in the classical conception of the spring brake mechanism is a secondary moment of braking forces, which is added to the main point of braking forces of the spring relative to the details of the braking. This secondary moment of braking forces applied during raising and lowering of the screen.

In the patent document EP-B-0 976 909 spring brake mechanism comprises an input part containing two teeth, the output item, also containing two teeth, the spring and the friction detail. The engine torque acting on the input item is transmitted to the output part through teeth, resting in one of the legs of the spring that rests on the tooth output details. Since the force acting on the output item is asymmetric, this leads to radial forces applied to the part, and thus creating a secondary moment of braking forces. In that case, the AE, when make every moment of forces to the output part, explain the phenomenon similar to the phenomenon of inhibition described in patent document FR-a-2 610 668. When this wave output part rests on the foot spring that locks this spring. In response to this asymmetrical force resulting radial force causes a shift in the output details up to the position in which it comes to rest in its guiding means.

The mode of functioning of classic designs spring brake mechanism such as those that were described in the previous examples, has disadvantages in some configurations. Indeed, in the case when the driving mechanism causes the screen to move in the direction of its descent, that is, in the case when the moment of force of the load acting in the own weight of the screen on the level of output detail oriented in the same direction as the engine torque of the drive mechanism acting on the level of the input items, adding this secondary moment of braking forces to the main point of braking forces is favorable because it reduces the reaction time of the brake mechanism, which increases the security of this installation. But the existence of this secondary moment of braking forces in the process of raising the screen, so far the case, when the moment of force of the load acting in the own weight of the screen on the output level of detail is opposite to the torque motor of the drive mechanism acting on the level of the input parts is particularly unfortunate, since the brake mechanism continuously exerts an inhibitory effect that makes one to give the engine excessive dimensional parameters. This engine should not only raise the load, but also to compensate for the secondary moment of braking forces that are in addition to the moment of force of the load.

This invention features an electric drive mechanism with a spring brake mechanism, improve the functioning of the preceding brake mechanisms, while retaining all their advantages. In order to optimize the dimensional parameters of the engine, in the present invention seeks to eliminate the aforementioned secondary moment of braking forces in the process of lifting the load. For this purpose, the present invention relates to an electrical drive mechanism, designed for the propulsion of the screen used in the home, which is moved between its open position and a closed position, and this drive mechanism with a spring brake mechanism, which is the meet in its composition:

- helical spring, each end of which forms the foot, passing in the radial direction or in the axial direction relative to the Central axis of this spring;

- detail of friction, containing essentially cylindrical surface friction, which is based in the radial direction at least one turn of the mentioned coil springs;

- input part, driven by electric motor of the drive mechanism and is able to come into contact with at least one leg of the spring in such a way as to bring the spring into rotational movement about the Central axis of the brake and in the direction of reducing the contact force between the said helical spring and the friction surface;

- output item associated with the screen and is able to come into contact with at least one foot above mentioned springs in such a way as to bring the spring into rotational movement about the Central axis of the braking and direction, allowing to increase the contact force between the helical spring and the friction surface.

In this drive mechanism, in the process lowering the screen, input the item brings spring into rotational motion with a decrease of the contact efforts so that the output item was released on Prasat is linoma movement, without direct contact between the input part and output part. In accordance with the invention mentioned input part includes at least two contact surfaces, capable of transmitting torque of the engine when lifting the screen by direct contact with at least two corresponding contact surfaces of the output details.

This screen creates a moment of force of the load on the output level of detail, and this moment of forces allows you to create a secondary moment of braking forces. Therefore, this drive mechanism specifically adapted for the screen with the vertical movement, its own weight which allows you to create the above-described moment of force of the load. This may be the winding of the curtain around the pipe or the turning of the garage door between the horizontal position and vertical position.

The input part and the output part are in direct contact only in the process of raising the screen. Thus, during lowering of the screen, these two parts are not in direct contact for transmission of engine torque. Indeed, when performing this maneuver input item releases the brake, acting on only one leg of the spring. When this torque of the engine affects the and the foot. And there is no force transmission between the input part and output part. As for the output part, she held the other leg of the spring. Consequently, it applies the force moment created by the force of the load, only to the foot in such a way as to bring the spring into rotational movement about the Central axis of the brake mechanism and in a direction that allows you to increase the contact force between the helical spring and the friction surface.

In the proposed description, the expression "direct contact between the two parts" means that one part affects another part or as a result of direct interaction of complementary surfaces, or as a result of the interaction between complementary surfaces through another hard part, located between these surfaces, or a combination of the interactions of the two previous types. Direct contact may be provided with one or more contact surfaces located on the output part, and one contact surface is a surface on which can be based complementary contact surface of the input part or complementary to the contact surface of the intermediate parts exposed to input details. D is I the implementation of the present invention must, to the moment of forces transmitted through at least two contact surfaces of the output details.

Balancing the torque of the engine, allowing to reduce the secondary moment of braking forces when lifting, can be sophisticated and implemented accordingly by transmitting torque through several sets of contact surfaces located with respect to the rotation axis of the spring so that the engine torque is transmitted through the substance in a balanced way, making the output item is only slightly tense in the radial direction. Indeed, these sets of contact surfaces can be located around the axis of the output parts in such a way as to reduce or even completely eliminate the occurrence of radial forces. For example, the moment of forces can be transmitted by the two contact surfaces of the output details are essentially identical and diametrically opposite with respect to the axis of this output details. This technical solution is quite simple to implement.

The preferred way of operation of the brake mechanism is identical in either direction of the torque motor used to lift the screen. This feature allows you to receive multi-function drive is echanism, which can be set regardless of the configuration screen. So, for example, for a tubular drive mechanism inserted in the tube winding, the operation of this drive mechanism is identical as in one, and in another, opposite, direction winding the screen. It is a symmetric function of the brake mechanism allows to rationalize the series and to facilitate the installation of the drive mechanism, since there is no need in a specific way to make a distinction in how you install the engine in relation to the screen.

In accordance with another specific, but not a mandatory aspect of the invention is:

in the absence of engine torque output item affects one leg of the spring in such a way as to bring the spring into rotational movement about the Central axis of the brake mechanism and in a direction, which can increase the contact force arising between the spring and the friction surface;

- at the level of the at least one contact surface in direct contact between the input part and the output part is realized through the hard parts, such as legs of the spring;

- the location of the contact surfaces allows to provide balancing power transmission PTO is NTA engine on raising so to cancel or substantially reduce the radial component relative to the axis of rotation of the spring, the forces transmitted to the output item;

two of the contact surface of the output details are diametrically opposite relative to the axis of this output details.

It is possible to provide that the output item was able to get in touch with the item having the kinematics different from the kinematics of this output details, in particular with the item, rigidly associated with the item of friction or with an input item, in that case, when the radial force acts on the output item, and this radial effect only occurs during the lowering of the screen.

Output detail the preferred way has the possibility to enter in contact with the body of the centering this output part with respect to the input parts under the action of the radial component of the resultant moment of force of the load acting from the side of the screen during the lowering of this screen.

In addition, it is possible to provide that the output item went for rotational movement relative to input details. Indeed, the input part and the output part must be centered relative to each other. The input part and the output part can be centered relative to each other by means of a shaft passing SLE the relationship of these parts. This shaft is mounted squeezed follows in the input part or the output part and installed a sliding way in the other of these parts, respectively, in the output part or in the input details. This centering is quite simple to implement and compact. In this case, the subsystem formed by the input part and the output part, the preferred way is centered with respect to the workpiece friction. This centering can be implemented either by means of the output details, either by using the input part. The preferred way this subsystem is centered using the input part, because it can significantly reduce the vibration of the brake mechanism.

Figure 1 is a schematic view of the tubular structure of the drive mechanism in accordance with the invention, comprising a spring brake mechanism in accordance with the invention;

Figure 2 is a perspective view of the analysis of the spring brake, owned by the drive mechanism shown in figure 1;

Figure 3 is a schematic illustration in cross section showing the operation of the spring brake mechanism shown in figure 2, in the process of lifting the load;

Figure 4 is a schematic illustration pop in the river incision operation of the spring brake mechanism, shown in figure 2, during lowering of the load;

Figure 5 is a schematic illustration in cross section showing the operation of the spring brake mechanism from the current level of technology in the process of lifting the load;

- Fig.6 is a perspective view of the analysis of the second method of implementation of the spring brake, which can be owned by the drive mechanism shown in figure 1;

- Fig.7 is a perspective view of the analysis from a different angle some structural elements of the spring of the brake mechanism shown in Fig.6;

- Fig is a schematic illustration in a view from the end face in the direction of the arrow F, shown in Fig.6, with partial cross section, of the operation of the spring brake mechanism, shown in Fig.6, in the process of lifting the load, generating a moment of forces, oriented in antitelomerase the direction to output the details of the brake mechanism;

- Figure 9 is a schematic illustration similar to illustration, shown in Fig.6, the view from the side and in partial cross-section, the operation of the spring brake mechanism, shown in Fig.6, in the process lowering the load, generating a moment of forces, oriented in antitelomerase on the managing, on output the details of the brake mechanism;

- Figure 10 is a schematic illustration similar to illustration shown in Fig, on the form side and partial cross-section, the operation of the spring brake mechanism, shown in Fig.6, in the process of lifting the load, generating a moment of forces, oriented in the trigonometric direction, to output the details of the brake mechanism;

- 11 is a schematic illustration similar to illustration shown in Fig, on the form side and partial cross-section, the operation of the spring brake mechanism, shown in Fig.6, in the process lowering the load, generating a moment of forces, oriented in the trigonometric direction, to output the details of the brake mechanism.

Figure 1 schematically presents the tubular rotary drive mechanism 100 that is designed to bring into rotational movement of the pipe 1 winding, which may be wound to a greater or lesser extent, the canvas 2 overlapping holes Acting Pipe 1 is rotationally driven drive mechanism 100 with respect to an axis of rotation x-X, which is located horizontally in the upper part of the said holes. This hole About is, for example, a hole is made is in the wall of the building. The drive mechanism 100, the pipe 1 and the fabric 2 overlap together in a equipped with the engine unfolding of the flap.

The drive mechanism 100 includes a fixed cylindrical tube 101, which is mounted geared motor 102 containing the electric motor 103, the first stage 104 of the reduction gearing, a spring brake mechanism 105, the second stage 106 of the reduction gear and the output shaft 107, which acts on the end 101A of the pipe 101 and drives the wheel-crown 3, rigidly connected for rotational movement with the pipe 1.

Pipe 1 winding rotates about the axis x-X and the fixed tube 101 by means of two swivel connections. The crown-bearing 4 mounted on the outer peripheral part of the tube 101 in the immediate vicinity of its end V opposite end 101A, provides the first two mentioned rotary links. A second pivotal connection at the other end of the pipe 1 and are given in the Appendix figures.

The drive mechanism 100 also includes item 109 attachment that goes on the end of V and allowing for attachment of the drive mechanism 100 on the supporting base 5. This item 109 fastening additionally designed to cover the pipe 101, and also to hold the module 108 control electric power to the motor 103. is the control module is supplied with electricity via power cable 6 from the mains electrical supply.

In the process of functioning of the tubular drive mechanism 100, the motor-reducer 102 results in rotational movement of the shaft 107, which, in turn, results in rotational movement of the pipe 1 by means of wheel-crown 3. For example, in the case when the driving mechanism 100 is installed in the housing of the expandable damper, rotary motion of the shaft 103 entails opening or, on the contrary, the overlap of the holes Acting Valve 2 is moved in the vertical direction in the hole between the top Of an open position and a lower closed position.

Figure 2-4 specifically illustrates the design of the spring brake mechanism 105 in accordance with the first way of implementing the present invention. As shown in figure 1, the rotor 103 results in rotational movement of the planetary gear of the first stage 104 of the reduction gearing. The drum 110 of this planetary mechanism, which holds three satellites, also forms the input part of the brake mechanism 105. This brake mechanism 105 includes a spiral spring 130, the coils of which centered on the axis X₁₃₀coinciding with the axis x-X in the case when this brake mechanism 105 is in place, as shown in figure 1. This spring is mounted in a compressed state inside the holes 141 part 140 of friction. G is saying in other words, the outer envelope 131 of the spring 130, which is defined by the outer forming it turns against the radial surface of the hole 141, resulting in a tendency to unite in a single whole, as a result of friction, springs 130 and workpiece 140.

Each end of the spring 130 forms a foot 132A, 132b, passing in the radial direction towards the axis X₁₃₀and towards the inside of the spring from its coils.

The input part 110 contains two tabs or "tooth" street 111A and 111b that is inserted inside the coil spring 130. Each ledge street 111A or 111b contains surface a or 113b able to be in contact respectively with the surface a first legs 132A, forming the first end of the spring, or surface 133b of the second legs 132b, forming the second end of the spring. Surface a is located so that the influence caused the rotation of the spring relative to the axis X₁₃₀in the direction opposite to the direction of rotation of the spring in the case when the effect is on the surface 133b.

The impact from the side of one of the teeth street 111A or 111b on the surface a or 133b causes a tendency to release the brake mechanism, i.e. to offset one of the legs 132A or 132b so that the radial stress between the outer envelope 131 of the coil spring 130 and the surface is completely friction holes 141 decreased. Indeed, it is the influence of one of the teeth street 111A or 111b tends to pull in the radial direction, the spring 130 about the axis x-X so that its outer envelope farther away from the surface of the hole 141. Item 110 allows, therefore, to influence the spring 130 in order to reduce the contact force between the spring and the friction surface of the holes 141. When this spring is able to rotate about the axis X₁₃₀which coincides with the Central axis of the X₁₀₅the brake mechanism 105, which itself, in turn, coincides with the axis x-X in the assembled configuration of the drive mechanism 100, are presented in figure 1. Here the direction or size is called "axial" in the case when the direction is or the size measured in the direction parallel to the axis X₁₀₅. Here, the radial direction is called in the case when the direction is perpendicular to and zechusim with respect to the axis X₁₀₅.

Against the input part 110 is output part 120 of the brake 105. This output item contains two loops a, s also inserted inside the coil spring 130. Ear a provided with two openings or hollow containers a, 122b, located on either side of this hole. Each cut a or 122b is intended to enter into it one the of the legs 132A, 132b spring and partially restricted when using the surface 124A beaches, 124b, able to be in contact with the surface 134a, 134b legs 132A, 132b. These surfaces 134a and 134b are respectively opposite surfaces a and 133b.

The impact on one of the surfaces 134a, 134b leads to a tendency to lead away from each other legs 132A, 132b, and the result is an expansion in the radial direction of the coils of the spring 130 with respect to the axis X₁₃₀and increase the contact force between the spring 130 and the surface friction of the hole 141. This is to bring the brake into action, that is, to the lock or to intensive braking of the rotational movement of the spring 130 with respect to the workpiece 140. Thus, the radial stress between the outer envelope 131 of the coil spring and the surface 141 of friction increases, which leads to lock in a fixed position or to intensive braking of the motion of the part 120 with respect to the axes X₁₀₅and X₁₃₀.

To this brake mechanism is operated, it is necessary to have an angular gap between the teeth of the street 111A and 111b of the input part 110 and the legs 132A and 132b of the spring. In addition, you must also have an angular gap between the ear a and legs 132A and 132b of the spring. To do this requires a certain width of the eyelet a. In addition, the axial length L₁₁₁or L ₁₂₁parts street 111A, 111b and a slightly exceeds the axial length L₁₃₀spring.

The output part 120 also includes a set of teeth 129 forming the surface interacting with the second stage 106 of the reduction gearing.

You need to be centering output part 120 with respect to the input part 110 is implemented through the shaft 118, which acts in the axial direction with respect to the input part from the location of the output part 120. This shaft 118 is a guiding tool for the output part through the hole 128, performed in the center of this output details.

As it is a more specific way should be of the types shown in figure 3 and 4, the load L, formed by the flap 2 can be regarded as an element rigidly connected with the output part 120 through the elements 1, 3, 106 and 107, which are represented by vertical dashed line shown in figure 3 and 4.

Own weight of the load L generates at the output the details of the moment of forces C_Lseeking to turn this output detail about the axis X₁₀₅in antitelomerase the direction shown on figures 3 and 4.

Here the position of the X₁₂₀designated the Central axis of the output part 120, which coincides with the axis X₁₀₅in the assembled configuration of the brake.

In the process of lifting the load L, and as schematically depict what Avelino figure 3, rotation in the above-mentioned antitelomerase the direction shown in figure 3, the output part 120, which is usually caused by the moment of forces C_Lthe load is blocked by the input part 110. This input part 110 is rotationally driven in the trigonometric direction, shown in figure 3, using torque With_Mproduced by the motor and balance the efficiency of the first stage 104 of the reduction gearing. Two ledge street 111A and 111b of the input part 110 rotates relative to the matching between the axes X₁₀₅and x-X up to a position in which one of the projections street 111A or 111b will be in contact with the surface 123A or 123b loops a output details. At this point another of these projections, 111b or street 111A, also comes in contact with one surface s or 123d second eyelet s output details. Consequently, the torque_Mthe engine is transferred to the output part through two sets of contact surfaces formed between the surfaces a and 113b and surfaces 123A and 123d, diametrically opposite relative to the axis X₁₀₅and to the axis X₁₂₀output details, resulting in a reduction or even complete elimination of the radial component of the resultant torque With_Mengine, vozdeistvuyushchego output part 120. Torque_Mthe engine is oriented in a direction opposite to the direction of the action of the moment of forces C_Lload. Thus, surfaces 123A and 123d form a contact surface of the output part 120.

Balancing efforts, subjected to the output part 120, illustrated in figure 3. Here the moment of forces C_Lload balanced by the efforts of the F_1aand F_1barising from, respectively, the stop between the surface 113d prong street 111A and the surface 123A of the ear e and emphasis between the surface 113d prong 111b and the surface 123d loops s. These two efforts F_1aand F_1bconverted to stress values of torque With_Mthe engine needed to overcome the moment of forces C_Lload. Since both of these efforts F_1aand F_1bhave essentially the same intensity and are essentially symmetrical relative to the Central axis X₁₂₀output components, the radial component of torque With_Mengine acting on the output part 120 has a negligibly small value or even zero. It should be noted that the shaft 118 of the input items, to ensure centering of the output part is not in contact with the hole 128 output details in this configuration, due to the fact that the radial component is mentioned above, the resultant has a negligibly small value.

To raise the load torque With_Mthe motor must exceed the sum of the moment of forces C_Lload and moment resistance force of the brake springs that occur due to the residual friction between the outer envelope 131 this spring and the friction surface of the holes 141. In the beginning of the movement the current torque With_Mengine should be a little more substantial as to release the brake 105 is necessary to overcome the force of static friction. Thus, ledge street 111A affects one of the legs of the spring, in particular the tab 132A, posted in the cut a, then the ear a is rotationally driven.

During lowering of the load L, and as is schematically presented in figure 4, rotation of the output part in antitelomerase direction in this figure doesn't stop using the input details, but is stopped by means of a spring 130. Thus, the moment of forces C_Lload presses the ear a to one of the legs 132A or 132b, and in this case the foot 132A. The consequence of this is the expansion in the radial direction of the coils of the spring 130 and the activation of the brake mechanism 105, as has already been said in the previous statement. The moment of forces C_Lthe loads acting on the part of the ear a on the surface 134a legs 132A, uravnovesena the tsya efficiency of the second stage 106 of the reduction gearing. When this tab 132A is inserted into the slot a. Torque_Mthe engine operates in the same direction as the moment of forces C_Lload.

Balancing efforts on the output details are illustrated in figure 4. The moment of forces C_Lload balanced two efforts F_2aand F_2b. The first force F_2acorresponds to the reaction of the surface 134a of the legs 132 of the spring 130 on the thrust surface 124A beaches cut a. Since this is the first effort F_2adoes not allow the integral to compensate for the moment of forces C_Lload, the output part 120 tends to continue moving in the direction perpendicular to the axis X₁₀₅relative to the previous reference configuration, up to the position in which this output item comes in contact with its guide means formed by the shaft 118 which is rigidly connected with the input part 110. Thus, the routing hole 128 output part comes in contact with the shaft 118, creating a second radial force F_2bthat allows you to balance the moment of forces C_Lload. This second force is F_2bcreates friction during movement of the load when lowering. This friction slows the load and added to the moment of braking forces of the spring. Thus, this friction contributes to the reactivity or performance tor the religious mechanism. His reaction is faster than the reaction time of the brake mechanism, for which this friction will not take place.

It should be noted that this way of implementing the input part 110 is centered with respect to the workpiece 140 friction due to the cylindrical cover, the envelope surface of which is not shown in the Appendix figures, communicates with a hole 141 items of friction. Consequently, the above-mentioned force F_2bcauses presented here is equivalent to the force arising between the input part 110 and part 140 of friction. This is equivalent to the effort involved in creating a secondary moment of braking forces and contributes to the reactivity of the brake mechanism.

To ensure the possibility of lowering the load, it is necessary to release the brake mechanism. This torque With_Mof the engine, results in rotational movement of the protrusions street 111A and 111b of the input part 110 up to the position in which the projection 111b is in thrust contact with the surface 133b feet 132b of the spring 130. The result of this action, the spring 130 is dissolved, and the output part 120 receives the opportunity to rotate due to the torque forces C_Lload. The parts 110 and 120 are not in direct contact.

If the direction of the us is tawania load is the opposite, the operation of this device is identical way. Thus, the operation of the brake mechanism is symmetric, which allows to simplify the installation of this brake mechanism, because its characteristics are the same in either direction of mounting of the drive mechanism, that is, whenever the direction of torque With_Mthe engine, which is used for lifting of the screen 2.

Figure 5 presents spring brake mechanism of classical type, known from the current level of technology, and, more specifically, illustrates its behavior when raising the load. Part of the brake mechanism, presented in figure 5, which are similar to the parts of the brake mechanism 105, are denoted by the same digital items, but reduced by 100. For the brake mechanism of this type the output item is not designed to balance the moment of the forces of the load when lifting. The output part 20 contains only one lug 21A. In the process of lifting the load, the operation of this brake mechanism is similar to the operation of the brake mechanism 105 in the configuration shown in figure 3. Torque_Mof the engine, results in rotational movement of the protrusion 11a up to the position in which the protrusion of the WMO is it in contact with the surface 33a of the legs 32A of the spring 30. The opposite surface 34a of this paws, for its part, is focusing in the surface 23a of the eye 21A of the output part 20 due to the moment of forces C_Lload. Consequently, the torque_Mthe engine is transferred to the output part 20 through the tabs 32A of the spring 30.

In the method of implementation in accordance with the invention described in the preceding statement with reference to figures 1 to 4, the engine torque is directly transmitted to the output part 120 through the contact between the surface a input part 110 and the surface 123A of the output components 120, and includes a presser spring is retracted in the lodgement a, specially provided for this purpose. This allows us to provide the best conditions for transmission of torque forces and less stress details.

In brake mechanism, presented in figure 5, the perception of the moment of forces C_Lload the leg 32A of the spring is not sufficient to balance the time and effort to create, thus, the radial force on the output part 20. This radial force causes movement of the output part up to the position in which it comes in contact with its guide means, which is implemented through holes 41 in the part 40 of friction. The output part 20 comprises a cylindrical cover, the envelope surface is rnost 25 which allows to provide a guiding influence in the hole 41. Thus, the moment of force of the load is balanced, on the one hand, through the efforts of the F'_1acorresponding to the stop lug 21A in the leg 32A of the spring 30, and on the other hand, using the efforts F'_1bresulting from the stop of the output part 20 into the hole 41 of the part 40 of friction. Taking into account that in the process of raising the load output part 20 has a relative speed with respect to the workpiece 40 friction, the force F'_1bthat creates friction in the process of movement corresponding to the lifting of the load. In order to lift the load L, the torque_Mshould, therefore, exceed the sum of the moment of forces C_Lload, the above-mentioned friction and, in the process of moving from the place, the moment of force needed to release the brake mechanism. Therefore, this friction adversely affect the determination of the dimensional parameters of the engine, because it should be more powerful in order to be able to compensate for the additional friction resulting from the efforts F'_1b.

When lowering the load, the operation of the brake mechanism is similar to its operation, is illustrated in figure 3 for the brake mechanism in accordance with the invention. But balancing efforts more like trim at the Eli, presented in figure 5. The movement of the load is braked by means of the moment of braking forces of the springs 30 and friction with the guide means formed by the hole 41 of the output details.

Figs.4 and 5 show two different guide means for the output part 20 or 120. In the first case, the output part 120 is directed toward the input part 110. At the same time, this input part 110 is centered with respect to the workpiece 140 friction. In the second case, the output part 20 is directed toward the workpiece 40 friction, which is stationary. Tests showed that the brake mechanism 105 behaves better in the first case. Indeed, centering the output of the part with respect to the input items can reduce the vibration of the brake mechanism.

Figure 6-11 illustrates the second method of implementation of the brake mechanism. The principle of its operation similar to the first method of implementation. The details of the brake mechanism indicated digital positions, similar to the digital positions of the first method of implementation, but increased by 100.

The output of the planetary gear of the first stage 104 of the reduction gearing results in rotational movement of the item 210, forming the entrance of the brake mechanism 105. The input part 210 provided with a polygonal shaft 219, designed to receive and transmit torque from the l, coming from step 104 of the reduction gearing. The brake mechanism 105 includes a helical spring 230, the coils of which centered on the axis X₂₃₀coinciding with the axis x-X in the case when this brake mechanism 105 is in place, as shown in figure 1. When the axes X₂₃₀and x-X coincide with the Central axis of the X₁₀₅this brake mechanism 105 in the assembled configuration of the drive mechanism 100 includes a brake mechanism 105 from this second method implementation.

The spring 230 is installed compressed into the holes 241 part 240 of friction. In other words, the outer envelope 231 spring 230, which is determined by forming the coils of this spring rests against a radial surface of the hole 241, which causes a tendency to unite in a single whole, as a result of friction, springs 230 and parts 240.

Each end of the spring 230 forms a foot a, 232b, passing in the radial direction towards the axis X₂₃₀and inside the spring, since it turns.

The input part 210 includes a protrusion or "prong" 211A that is inserted inside the coil spring 230 between the legs a and 232b. This prong 211A has two surfaces 213A, 213b, able to be in contact, respectively, with the surface a first foot a forming the first end of the spring, and with the surface 233b of the second legs 232b, forming the second to the end of the spring. Surface a is located so that the influence brought spring into rotational motion about the axis X₂₃₀in the direction opposite to the direction of rotation of the spring in the case when the effect is on the surface 233b.

The effects of the prong 211A on the surface a or 233b tends to release the brake mechanism, that is, to bring into rotational movement of the foot a or 232b respect to the axes X₂₃₀and X₁₀₅in this direction, so that the radial stress between the outer envelope 231 of the spring 230 and the surface friction of the hole 241 decreased. Indeed, the impact of tooth 211A on one of the surfaces a or 233b compress the spring 230 in a radial direction relative to axis x-X so that its outer envelope was removed from the surface of the hole 241. Thus, item 210, you can affect the spring 230 in order to reduce the contact force between the spring and the friction surface of the hole 241.

Against the input part 210 is output part 220 of the brake mechanism 105. This output item contains two loops a, 221b, also inserted inside the coil spring 230. Each eye is equipped with, respectively, a cutout or hollow lodgement a, 222b, intended to receive one of the legs a 232b of the spring 230. Each cut a, 222b limited surface a, 224b, able to be in contact with the surface 234a, 234b feet a, 232b. Surface 234a, 234b are respectively opposite surfaces a and 233b.

The impact on one of the surfaces 234a, 234b aims to bring together the tabs a, 232b, resulting in expansion in the radial direction of the coils of the spring 230 with respect to the axis X₂₃₀and increase the contact force between the outer envelope 231 of the spring 230 and the surface friction of the hole 241. This fact is expressed in the actuation of the brake mechanism, i.e. in the lock or heavy braking rotational motion of the spring 230 with respect to the workpiece 240. Thus, the radial stress between the outer envelope 231 of the coil spring and the braking surface 241 is increased.

At the same time, every ear a, 221b output part 220 includes the protruding portion a, 226b, passing in the axial direction towards the input details and is able to accommodate, respectively, the cut s, 216d, made in the shape of a banana in the input part 210, in the case where the brake mechanism 105 is assembled. These protruding parts a and 226b possess the dimensional parameters and are arranged so that one of their surfaces a, 227b was in contact with the inner surface is Yu s, 217d, bounding the corresponding hole s, 216d, in the case when the surface 213b, 213A prong 211A input part 210 is in contact with the surface 223b, a loops 221b, a output part 220.

On Fig and 10 illustrates two possible configurations of the brake mechanism 105. Determination of dimensional parameters holes s, 216d is such that, outside the two preceding configurations, the protruding portion a, 226b not rest in any internal surface of the hole.

To this brake mechanism is operated, it is necessary to have an angular gap between the tooth 211A input part 210 and the feet a and 232b of the spring. In addition, you must also angular clearance between the lugs a and 221b and legs a and 232b of the spring. To do this requires a certain width of the tooth 211A. In addition, the axial length L₂₁₁and L₂₂₁parts 211A, a and 221b slightly exceeds the axial length L₂₃₀spring.

The necessary centering of the output part 220 with respect to the input part 210 is implemented through the shaft 270. This shaft is inserted into the centered hole 218 of the input part 210. The part of the shaft 270 is from the output part 220.

On Fig-11 illustrates the operation of the brake mechanism 105. Fig and 9 correspond to the winding of the screen on the shaft 1 in antitelomerase direction or in EmOC is the t clockwise on these figures. On Fig illustrates the lifting of the load, while figure 9 illustrates the lowering of the load. Figure 10 and 11 correspond to the winding of the screen on the shaft 1 in the trigonometric direction or in the counterclockwise direction in these figures. Figure 10 represents the lifting of the load, while 11 represents the lowering of the load.

First time operation of the brake mechanism is explained with respect to the first configuration of the winding of the screen, that is, the winding of the screen clockwise Fig and 9.

With a certain lack of weight load L affects the item 220 in the form of the moment of forces C_Lthat presses one of the ears a or 221b, and in this case, the eyelet 221b, to one of the legs a or 232b, and in this case the foot 232b, as shown in Fig.9. The consequence of this is the expansion in the radial direction of the coils of the spring 230 and the actuation of the brake mechanism 105, as has already been said in the previous statement. The moment of forces C_Lacting from the side of the ear 221b on the surface 234b feet 232b, balanced by the efficiency of the second stage 106 of the reduction gearing. This moment of force represented by the vector associated with the ear 221b. Foot 232b when this is inserted into the cradle 224b.

In the process of lifting the load L, and how this performance is Avelino on Fig, the input part 210 is rotationally driven via the torque forces From the_Mproduced by the motor and balance using the coefficient of the first stage 104 of the reduction gearing. The protrusion 211A input details when it is rotated up to the position in which he will be in contact with the ear 221b output the details on the contact surface between the surfaces 213b and 223b. To raise the load torque With_Mshould, therefore, exceed the sum of the moment of forces C_Lload and moment resistance of the spring brake mechanism, resulting from the residual friction between the outer envelope of the spring and the friction surface of the hole 241. Here torque With_Mrepresented by a vector shown in dotted lines associated with the input item.

When moving from place affecting torque With_Mshould be more significant, since the release of the brake mechanism 105 is necessary to overcome the force of static friction. To release the brake mechanism 105 protrusion 211A affects the foot 232b, located in the neck 222b after ear 221b is rotationally driven. The transmission of torque From_Mthe engine from the input part 210 to the output part 220 osushestvlyaetsya a double contact. On the one hand, the surface 213b of the protrusion 211A rests on the surface 223b of the ear 221b. And, in a diametrically opposite position, the inner surface s holes s rests on the surface a protruding part a. Thus, the moment of forces C_Lload balanced by efforts of the F_1aand F_1bdue emphasis between parts 211A and 221b, on the one hand, and parts C and e, on the other hand. Because these two efforts have essentially the same intensity and are essentially symmetrical relative to the Central axis X₁₀₅the brake mechanism 105 and to the axis X₂₂₀output components, the radial component of the resultant torque With_Mon the output part has a negligibly small value or even practically zero. Surface 223b and a form a contact surface output details.

During lowering of the load L, and as schematically illustrated in figure 9, the rotation of the output part 220 does not stop using the input part 210, but is stopped by means of a spring 230. Thus, the moment of forces C_Lload presses the ear 221b to one of the legs a or 232b, in this case to the foot 232b. The consequence of this is the expansion in the radial direction of the coils of the spring 230 and the actuation of the brake mechanism 105, as this is m has already been said in the previous statement.

The moment of forces C_Lacting from the side of the ear 221b on the surface 234b feet 232b, balanced by the efficiency of the second stage 106 of the reduction gearing. Foot 232b is inserted into the cradle 222b. Torque_Mthe engine has the same direction as the moment of forces C_Lload. When this balance is non-equilibrium, provided in the process of lifting the load. The moment of forces C_Lload balanced by efforts of the F_2aand F_2b. The first force F_2acorresponds to the reaction of the spring, blocking the load at surface level interaction between the surface 234b feet 232b of the spring 230 and the supporting surface 224b of the recess 222b loops 221b output details. Since the first force F_2adoes not allow to compensate for the moment of forces C_Lload, the output part 220 tends to rotate relative to the previous reference configuration up to the position in which the output item will be in contact with its guide means formed by the shaft 270, rigidly connected with the input part 210. Thus, the routing hole 228 output part 220 with respect to the shaft 270 is in contact with this shaft 270, creating a second force F_2bthat allows you to balance the moment of forces C_Lload. This effort is dialnum with respect to the axis X ₂₂₀. This force F_2bcreates friction during movement of the load L in the direction of its sinking. This friction slows the load and added to the moment of braking forces of the spring. It helps, therefore, the reactivity of the brake mechanism. While the reaction time of this brake mechanism is faster than the reaction time of the brake mechanism, for which such friction will not take place.

It should be noted that this way of implementing the input part 210 is centered with respect to the workpiece 240 friction due to the cylindrical shell, the envelope surface of which is not represented here, interacts with the hole 241 parts of friction. Consequently, the above-mentioned force F_2bcause equivalent effort, not presented here, between the input part 210 and part 240 of friction. This is equivalent to the effort involved in creating a secondary moment of braking forces, contributing to the reactivity of the brake mechanism.

To ensure the possibility of lowering the load, it is necessary to release the brake mechanism. This torque With_Mof the engine, results in rotational movement of the protrusion 211A input the details up to the position in which this ledge will be limited by the surface a the of agriculture production a spring 230. The result of this action, the spring 230 is dissolved, and the output part 220 receives the opportunity to rotate due to the torque forces C_Lload, and parts 210 and 220 are not in direct contact.

The operation of the brake mechanism in accordance with the second winding configuration illustrated in figures 10 and 11.

When lifting the load, and as shown in figure 10, the moment of forces C_Lload balanced by efforts of the F_1aand F_1barising from, on the one hand, the contact between the surface 213A of the tooth 211A and the surface a loops a, and on the other hand, as a result of contact between the inner surface 217d holes 216d and the surface 227b protruding part 226b. Because these efforts F_1aand F_2aare balanced, the radial component of the resultant torque With_Mon the output part 220 is negligible. Thus, the engine must produce a torque greater than the moment of forces C_Lload, to which is added, only the moment of forces of resistance of the brake mechanism, which is a consequence of the friction between the spring 230 and part 240 of friction. Thus, secondary moment of braking forces resulting from friction between the output part 220 and guide shaft 270, one is by a relatively small or completely absent. Surface a and 227b form a contact surface output details.

In lowering the load, the moment of forces C_Lthis load is balanced by efforts of the F_2aand F_2b. The first force F_2acorresponds to the reaction of the spring 230, blocking the load L at the surface level of interaction between the surface 234a feet a spring 230 and the bearing surface of a cut a loops a. The second force is F_2bcorresponds to a force localized at the level of the guide shaft 270 output part 220, while parts 210 and 220 are not in direct contact. This friction creates a radial force that retards the motion of the load. Thus, the brake mechanism reacts quickly enough, because the secondary moment of braking forces no longer becomes negligibly small.

These two ways of implementation describe the spring brake mechanism, the ends of which are bent towards the inside of this spring. Of course, these tips can be oriented in an outward direction. Another embodiment consists in bending the ends of the said springs in a direction parallel to the Central axis of this spring. These legs are held in the axial direction from one to the other side of the spring, away from the center this spring.

In addition, the spring brake mechanisms which should not be placed in a specific way between the two steps of the reduction gearing. It can be located on the motor output or the output of the reduction gearbox.

1. An electric drive mechanism (100) the propulsion of the screen (2), used at home, which is moved between its open position and a closed position, with a spring brake mechanism (105), which is composed of:
the spiral spring (130; 230), each end of which forms the foot (132A, 132b; a, 232b), passing in the radial direction or in an axial direction relative to the Central axis (X₁₃₀; X₂₃₀) this spring;
- item (140; 240) friction, containing essentially cylindrical surface (141; 241) friction, which is based in the radial direction, at least one coil of the aforementioned coil springs;
- input part (110; 210), driven by electric motor (103) of the drive mechanism and configured to come into contact with at least one foot (132A, 132b; a, 232b) of the spring in such a way as to bring the spring into rotational movement about the Central axis (X₁₀₅) brake and direction, allowing you to reduce the contact force between the helical spring and the friction surface;
- output part (120; 220)associated with screen (2) and executed with the opportunity to come in contact with, ENISA least one foot (132A, 132b; a, 232b) of the said spring thereby to bring the spring into rotational movement about the Central axis (X₁₀₅) the brake mechanism and in a direction that allows you to increase the contact force between the helical spring and the friction surface,
where in the process of lowering of the screen referred to the input part (110; 210) causes the spring (130; 230) into rotational motion with a decrease of the contact efforts so as to ensure the release of the output parts (120; 220) for rotational movement without direct contact between the input part and the output part,
characterized in that the said input part (110; 210) contains at least two contact surfaces (a, 113d; 213b, s)made with the possibility to transfer torque (C_M) engine when lifting the screen (2) as a result of direct contact with at least two corresponding contact surfaces (123A, s; 223b, a) output details (120; 220).

2. Electric drive mechanism according to claim 1, characterizedthe fact that the behavior of the brake mechanism (105) is the same for any direction of torque (C_M) of the motor for raising the above screen (2).

3. Electric drive mechanism according to one of paragraphs. 1 or 2, characterized in that,in the absence of engine torque output part (120; 220) provides the force per foot (132A, 232b) spring (130; 230)that this spring is rotationally driven relative to the Central axis (X₁₀₅) brake mechanism, which allows to increase a contact force between the spring and the surface (141; 241) friction.

4. Electric drive mechanism according to one of paragraphs. 1 or 2, characterized in that at least one contact surface in direct contact between the input part (110; 210) and the output part (120; 220) is realized through the hard parts, such as legs (132A, 132b; a, 232b) spring (130; 230).

5. Electric drive mechanism according to one of paragraphs. 1 or 2, characterized in that the location of the contact surfaces (a, 113d, 123A, 123d; 213b, 223b, s, a) allows you to balance transfer torque (_M) engine lifting thus, to cancel or substantially reduce, the radial component relative to the axis (X₁₀₅) rotation springs (130; 230), efforts transferred to the output part (120; 220).

6. Electric drive mechanism according to one of paragraphs. 1 or 2, characterized in that the two contact surfaces 123A, 123d; 223b, a) output details (120; 220) are diametrically opposite relative to the axis (X₁₂₀; X₂₂₀this output details.

7. Electric drive mechanism for demo of PP. 1 or 2, characterized in that the output part (120; 220) is configured to come into contact with the part (118; 270)with the kinematics different from the kinematics of this output details, in particular with the item, rigidly associated with the item (140; 240) friction or with an input part (110; 210), in the case when the radial force acts on the output item, and this radial force is created only in the process of lowering the mentioned screen (2).

8. Electric drive mechanism according to one of paragraphs. 1 or 2, characterized in that the output part (120; 220) is made with the ability to go straight to the body (118; 270) centering the output of the part with respect to the input part (110; 210) under the action of the radial component of the resultant torque (C_L) loads acting on the part of the screen (2) in the process of lowering of the screen (2).

9. Electric drive mechanism according to one of paragraphs. 1 or 2, characterized in that the output part (120; 220) is sent by the rotational movement relative to the input part (110; 210).

10. Electric drive mechanism according to one of paragraphs. 1 or 2, characterized in that the subsystem formed by the input part (110; 210) and the output part (120; 220), centered in relation to the workpiece (140; 240) friction.