FI128197B - Impact device for cleaning of surfaces, such as heat delivery surfaces - Google Patents

Abstract

The present invention relates to a percussion device for cleaning surfaces, such as thermal surfaces, comprising a body (1), a hammer body (8), an anvil assembly (7), actuating means for displacing a hammer body (8) back and forth on the body (1) and a spring impact energy from the hammer body (8) to the anvil unit (7). In order to easily and extensively adjust the impact force and frequency of the impactor, and in addition to dispense with the use of springs to move the hammer body (8) while lightening the impactor, the impactor body (1) comprises a first gas chamber (100) defining an impact chamber; ), the impactor actuating means for moving the hammer body (8) comprises a gas pressure accumulator (105) for supplying gas to the first gas space (100) so that the gas pressure of the first gas space is greater than the gas pressure of the second gas space (101); the force exerted on the hammer body (8) is greater than the opposite force exerted on the hammer body by the gas pressure (P2) in the first gas space (100). The drive means for moving the hammer body 8 back and forth obtain their gas pressure from the same source of compressed gas.

Description

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Impact cleaner for cleaning surfaces such as thermal surfaces

Background of the Invention

The invention relates to a percussion device for cleaning surfaces, such as thermal surfaces, comprising the percussion device

- body,

- a hammer body arranged to be reciprocally movable on the body between the first end position and the second end position, and comprising a first end surface and a second end surface opposite to the first end surface,

- an anvil assembly adapted to receive the impact energy of the hammer as the hammer hits the abutment surface of the anvil,

- actuating means for displacing the hammer body back and forth on the body between a first extreme position with one end surface of the hammer body at a maximum distance from the anvil unit abutment surface and a second extreme position where the hammer body strikes the anvil unit;

a spring adapted to transmit the impact energy from the hammer to the anvil assembly.

In the second extreme position where the hammer body strikes the anvil unit, the hammer body 20 is naturally in contact with the anvil unit abutment surface.

In particular, the above-mentioned impactor is intended to be used to clean heat surfaces such as boiler walls, convection packages and heat exchanger surfaces from soot and other dirt that accumulates on the heat surfaces in use.

Such an impact device is known from EP-A-2643104. This known impact device comprises a spring by which the hammer body is struck towards the lower part by a spring force. In applications that require the hammer member to strike the lower portion with high impact energy in order to effectively clean the heat surface, the spring must have a high spring force, which in practice means that the spring must be large. A large spring increases the size and weight of the natural impactor. In practice, this known impact device does not allow for extensive control of the impact force, since the impact force is practically determined by the spring elastic force, which is specific to the spring, limiting the control of the impact force within the characteristics of the selected spring.

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Brief Description of the Invention

It is therefore an object of the invention to provide a new impactor which eliminates the limitations of use associated with known impactors and which allows for easy adjustment of the impactor operation with the thought of impact force and stroke frequency. To achieve these 5 objects, the impactor of the invention is characterized in that:

- the body comprises a first gas valve defining an impact chamber and a second gas valve defining a return pressure chamber, wherein the first end surface of the hammer body is limited to the first gas space and the second end surface of the light piece is limited to the second gas space;

- actuating means for moving the hammer member from the first end position to the second end position, comprising a pressurized gas source adapted to pressurize the gas pressure accumulator adapted to charge the gas from the pressurized gas source through the supply line the hammer body being greater than the opposing force exerted by the gas pressure in the second gas space on the hammer body, the drive means further comprising degassing means for relieving gas from the second gas space as the hammer body moves toward the lower portion comprising the degassing line;

- actuating means for moving the hammer body from the second extreme position to the first extreme position, comprising gas pressure and force adjusting means to provide a second gas pressure applied to the hammer body greater than the opposing force applied to from the extreme position to the first extreme position. Preferably, the gas pressure and force control means comprise gas supply means for feeding gas to one of their gases Preferably the gas pressure and force control means comprise gas supply means for supplying gas with another gas, since such gas pressure and force control means are easily implemented

Preferably, the hammer body is a piston-like member, and the impactor body defines a cylindrical space for the hammer body, which encloses

20185506 prh 15 -05-20199 first gas space and second gas space. Such a piston-cylinder type impactor is simple in manufacture.

Preferably, the gas supply means are adapted to supply gas through the third valve to the second with their gases, wherein the gas supply means are adapted to receive gas pressure from the same source of pressure gas as the gas pressure accumulator.

Preferably, the impactor gas pressure accumulator surrounds the cylindrical space. This allows the size of the impactor to be small, which is important especially in areas with limited impact space. Preferably, then, the gas 10 pressure accumulator is a tubular space surrounding a cylindrical space. The latter enables easy manufacture of the impactor.

An essential feature of the invention is that the displacement of the hammer body back and forth is based on the fact that the displacement is performed by gas pressure, whereby the springs for moving the hammer body can be dispensed with.

Preferred embodiments of the invention are set forth in the dependent claims.

The major advantage of the impactor according to the invention is that its impact force and frequency are easily and widely adjustable. In addition, the use of springs for moving the hammer piece can be dispensed with, thus making the impactor light. Another advantage is that it has no breakable springs.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will now be described in more detail by way of a preferred embodiment with reference to the accompanying drawings, in which: Figure 1 shows a first impact position of the impactor with the hammer body in the first end position; Figure 2 shows the first impact position of the impactor Figure 4 illustrates a second intermediate position of the impactor in which the impactor hammer is moving back to its first extreme position, and Figure 5 schematically shows the impactor of Figures 1-4.

DETAILED DESCRIPTION OF THE INVENTION

The impactor of Figures 1 to 4 comprises a body 1 on which the hammer head 8 is adapted to move back and forth between the first end position and the second

20185506 prh 15 -05-20199 between the stern positions. Figures 1-4 show different operating positions of the impactor. In the operating position of Figure 1, the hammer body 8 is in the first extreme position, and in the operating position of Figure 3, the hammer body is very close to its second extreme position. Figures 2 and 4 show two different intermediate positions of the impactor.

The hammer body 8 of the impactor is a piston-like member comprising a first end face 102 and a second end face 103 opposite to the first end face. The body 1 of the impactor is cylindrical, the hammer body 8 and the body 1 forming a cylinder piston assembly. Body 1 defines a cylindrical space enclosing en10 first gas valve 100 and second gas valve 101 disposed on opposite sides of hammer body 8. The first gas body 100 delimits first end surface 102 of hammer body 8 and cylindrical space of body 1; after all, the second gas 101 defines a second end surface 103 of the hammer body 8 opposite to the first end surface 102 and a cylindrical space of the body 1.

The anvil unit 7 of the impactor comprises an anvil body 7a and an anvil portion 7b mounted on the impactor body 1. The lower body 7a has a flange 7c to which the first end 4 of the impactor body 1 is secured by a plurality of elongated members 3 which allow the body 1 to flex with the anvil body 7a, preferably in the longitudinal direction of the anvil body. The elasticity is implemented by means of springs (not shown) associated with the elongated members 3. For simplicity, the flange 7c and the elongated members 3 are shown only in Figure 1. The lower part 7b is adapted to move on the body 1 and receive the impact energy of the hammer member 8 when the second end face 103 of the hammer .

Between the lower part 7b and the anvil body 7a there is a spring 6, which according to the figures is preferably formed by two or more opposing plate springs (the figures have two plate springs facing each other). The spring 6 transmits impact energy from the anvil member 7b to the anvil body 7a. As the anvil member 7b moves towards the spring 6 due to the impact of the blade body 8 on the body 1, it is resilient. Because of the low elasticity of the spring 7, the displacement of the lower part 7b in the body is also slight. Preferably, all of the impact energy received by the anvil member 7b is transmitted to the anvil body 7a via a spring 6, whereby the anvil member 7b does not directly hit the anvil member 7a. It is conceivable that the anvil member 7b directly contacts the anvil 35 body, but the force of this hit is only a small fraction of the impact force exerted by the spring 6 on the anvil member 7b to the anvil body 7a.

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The sizes of the first gas space 100 and the second gas space 101 are determined by the position of the hammer body 8 in the body 1, cf. Figures 1-4. With the hammer piece 8 in the position of Figure 1. When the second end surface 103 of the hammer body 8 is at a maximum distance S1 from the stop surface 107 of the lower part 7b, the volume of the second gas space 101 is at its maximum and the size of the first gas space 100 is very small or zero; and when the hammer body 8 is in the position of Figure 3, its second end surface 103 is closed or nearly closed on the abutment surface 107 of the lower part 7b, wherein the volume of the first gas space 100 is maximum and the volume of the second gas space 101 is very small or zero. In the gap positions of the hammer body 8 shown in Figures 2 and 4, the volumes of the first gas space 100 and the second gas space 101 are roughly equal. In Figure 2, the hammer body 8 is moving toward the anvil 7, and in Figure 4, the hammer body is moving away from the anvil.

The reciprocating movement of the hammer part 8 of the impactor is achieved by means of actuating means comprising a pressurized gas source 104 and gas supply lines to the valves 15, which will be described below.

The impact energy for moving the hammer body 8 from the position of Figure 1 to the position of Figure 3 is provided by abruptly pressurizing the first gas space 100 with pressure P2, as a result of which the hammer body 8 moves and strikes the lower part 7b. The gas space 100 is preferably pressurized with air, but other gas or gas mixture suitable for 20 applications may be used instead of air. It can be said that the first gas space 100 defines the impact chamber. Said pressure P2 is obtained by its first gases 100 from a gas pressure accumulator 105 pressurized with a pressure P1, for example 4-6 bar. The gas pressure accumulator 105 surrounds the impactor body 1 tubularly or cylindrically. Reference numeral 25 110 indicates connecting channels for the first valve 109 to the gas pressure accumulator

105 and first gas space 100. The gas may be led from the gas pressure accumulator 105 through the interconnecting conduits 110 to its first gases 100. The gas accumulator 105 is charged before discharge to said pressure P1 with gas from the propellant source 104 via the conduit 115 and the first valve 109. When the gas pressure accumulator 105 is charged, the closing portion of the first valve 109 is moved by the gas pressure of the supply line 115 to the left toward the hammer member 8, thereby closing the conduits 110 between gas pressure accumulator 105 and first gas space 100 . Preferably, the closure portion of the first valve 109 is a rubber-made closure

20185506 prh 15 -05-20199 a bullet which, under pressure from a pressurized gas source 104 (pressure of about 4 bar or more), moves from the position shown in Figure 1 toward the hammer member 8. If the pressure of the first gas 100 is greater than gas pressure in feed line 115 .

Reference numeral 108 indicates a depressurization duct connecting the first gas 100 to the outside air. The pressure relief conduit 108 is small in size to prevent a significant amount of gas exiting from the first gas chamber 100 as the hammer body 8 moves toward the anvil unit 7. If the gas was rapidly and rapidly exited from the first gas chamber 100 to the pressure relief channel 108 when it hits the anvil 7. The purpose of the pressure relief conduit 108 is to expel gas from the gas space to the environment when the hammer body 8 is moved to the right towards the second end 5 of the impactor body, the first gas 100 being less than the second gas 101. The pressure outlet channel 108 is preferably provided at the second end flange 2 of the housing.

When it is desired that the hammer body 8 be struck toward the anvil assembly 7, the pressure P1 of the gas pressure accumulator 105 is released through the connecting conduits 110 associated with the first valve 109, thereby exerting a pressure P2. The pressure P1 of the gas pressure accumulator 105 may be called the charge pressure before the pressure of the gas pressure accumulator is released. The pressure P1 of the gas pressure accumulator 105 is released by decreasing the pressure in the supply line 115, as a result of which the closure portion of the first valve 109 moves from the hammer body 8, i.e., to the right before the hammer body 8 moves towards the anvil 7, the pressure P3 of the gas in the second gas space 101 is typically about 1 bar. In practice, the pressure difference P1-P3 between the first gas 100 and the second gas space 101 causes the hammer body 8 to move and strike the lower part 7b.

Figure 2 illustrates the displacement of the hammer body 8 towards the anvil unit 7. As the hammer body 8 moves towards the anvil unit 7, the volume of the first gas 100 increases and its pressure decreases. As the hammer body 8 moves to the left, gas from the second gas chamber 101 is evacuated through the degassing line 106 so that the pressure of the other gas 101 is not increased 35 so as to prevent rapid and vigorous transfer of hammer body 8 to lower part 7b.

20185506 prh 15 -05-20199 before the hammer hits the lower part. The acceleration of the hammer body 8 in the body 1 can typically be from 6 to 10 m / s ² . The gas exits the degassing line 106 through the third valve 111. The third valve 111 is a quick-release valve that allows rapid gas discharge from line 106. The third type of valve 111 is a three-way valve. The third valve 111 is opened shortly before the gas pressure accumulator 105 is discharged, thereby providing the first gas chamber 101 with a rapid gas discharge.

In Figure 3, the hammer body 8 has struck the anvil member 7b and transmitted its impact energy through a spring 6 to the anvil body 7a and is beginning to move away from the lower member 7b (right) toward the second end 5 of the body 1 101 controls a gas pressure that exceeds the first gas state

100 pressure of the prevailing gas. FIG. . A high gas pressure is not required to move the hammer body 8 towards the first extreme position shown in Figure 1, since the pressure of the first gas 100 is low due to escape of gas through the pressure relief conduit 108; the pressure required for the transfer may be, for example, 1.5 to 2 bar. The pressure relief component 112 ensures that the pressure supplied by the compressed gas source 104 to one of its gases

101 drops to the desired value.

The gas pressure for returning the hammer body 8 from position 1 to position 3 in Figure 3 is thus obtained along the same degassing line 106 used to remove gas from the second gas space 101.

Thus, the operation of the first valve 109 and associated connecting ducts 110 is as follows: when the closing member of the first valve 109 is at a level 30, gas can flow from the gas pressure accumulator 105 to the first space 100 but not to the feed pipe 115 (thereby imparting impact to hammer 8); when the first valve 109 closes on the left at night, gas can flow from the feed line 115 to the gas pressure accumulator 105 but not to the first space 100 (whereby the gas pressure accumulator 105 is charged to the charge pressure).

The recovery time of the hammer body 8 is achieved by adjusting the pressure exerted by the pressure relief component 112. The recovery time can preferably

As the hammer body 8 moves toward the second end 5 of the impactor, the gas can escape from the impactor through the first depressurization channel 108 associated with its first gas 100. Because one of the gases 101, in fact the gas pressure therein, acts to return the hammer body 8 back to its first extreme position, the other of the gases 101 defines a return pressure chamber.

Reference numeral 113 indicates a fourth valve for supplying gas from a pressurized gas source 104, optionally to a gas pressure accumulator 105 via a supply line 115 or to another of its gases 101 via a degassing line 106. The fourth valve 113, which is preferably a three-way valve, is a stroke control valve (pressure-Δ10 divider). A fourth valve 113 ensures that the first valve 109 remains in the position shown in Figure 1 during the stroke.

A fifth valve 114 is provided on the feed line 115 to control the delay. Preferably, the fifth valve 114 is a resistive counter valve adapted to control the pressure in the feed line 115 so that the third valve 111 opens before the first valve 109. The fifth valve 114 provides resistance to the flow of gas from the first valve 109 to the fourth valve 113; flow from the fourth valve 113 to the first valve 109. The fifth valve 114 slows down the release of gas pressure in the feed line 115 to the environment, i.e. the atmosphere.

The impactor includes a control unit 120 that controls at least the valve

113 activities. The control unit may further be adapted to control one or more of the valves 109,111,112 and 114 so as to effect the impactor. At least some of the latter valves may also be manually operable. By the desired operation, it is meant that the stroke energy on the anvil 7 and 25 is struck at the stroke frequency so that it is suitable for the operating environment in which it is used.

The invention has been described above with only one preferred embodiment and it is therefore noted that the invention can be implemented in many ways within the scope of the appended claims. Thus, for example, the gas pressure accumulator 105 need not consist of a tubular space surrounding the cylindrical space defined by the body 1, but the gas pressure accumulator may be a space attached to the body that does not surround the cylindrical space; the gas pressure accumulator may even be separate from the body. However, it is highly recommended that the gas pressure accumulator surrounds the impactor body 1 and the cylindrical space to form a tubular pressure accumulator, since such a gas pressure accumulator occupies little space and does not add much space to the impactor. The compact impactor is easy to install9

20185506 prh 15 -05-20199 for different applications. It has been shown above that the same compressed gas source 104 is included in the drive means for moving the hammer body from both the first end position to the second end position and vice versa from the second end position to the first end position. This is highly appropriate, but it is conceivable not to use the same compressed gas source for said displacements of the hammer, wherein the first compressed gas source is used to move the hammer from the first to the second extreme and the second compressed gas source to move the hammer from the second to the first. However, the latter arrangement is more complex than the arrangement described. Accordingly, it is also conceivable not to use the same degassing line 106 to supply gas to one gas space 101 as to remove gas from another gas space. However, using the same degassing line 106 is advisable in order to avoid unnecessarily increasing the number of components of the impactor and to keep the structure of the impactor simple. It is also conceivable that the displacement of the hammer body 8 towards one end 5 of the impactor body is effected by sucking gas out of the first gas space, preferably by combining vacuum means (not shown) with pressure relief conduit 108. The gas pressure (via the degassing line 106) needs to be controlled to move the hammer body 8 to the right. In the detailed description of the invention, the anvil assembly 7 comprises an anvil body 7a and an anvil member 7b spaced between a spring 6. Instead, the spring 6 may be disposed between the hammer member 8 and anvil member 7 such that the spring 6 is located on the impactor body 1 and an anvil body 7a) and its end is disposed within the impactor body 1 so that it can slightly shift relative to the longitudinal direction of the impactor body 1, i.e. the impact direction of the hammer body 8.

The following is a list of the entries used in the drawing.

frame

2 end flange elongated members first end of impactor body 1 second end of impactor body 1 spring

7 anvil unit

7a anvil frame

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7b lower part

7c flange hammer (preferably piston-like member)

100 first gas chamber (impact chamber)

101 second gas chamber (return pressure chamber)

102 first end surface of hammer piece 8

103 one end surface of hammer piece 8

104 compressed gas source

105 gas pressure accumulator

106 degassing line (may additionally serve as a gas supply line)

107 anvil unit 7 abutment surface (anvil portion 7b abutment surface)

108 pressure relief duct

109 first valve

110 connecting ducts between first gas valve 109 and first gas chamber 100 and between first gas pressure battery 105 and supply line 115 associated with first valve 109

111 third valve (quick release valve, preferably three-way valve)

112 pressure relief component (preferably pressure relief valve)

113 Fourth Valve (Impactor Control Valve; Preferably Three-way Valve)

A fifth valve (preferably a resistive valve) in the feed line 115

115 feed line

120 control unit

P1 is the gas pressure of the gas accumulator 105

P2 is the gas pressure of the first gas space 100

P3 is the gas pressure of the second gas space 101

Claims (13)

1. impactor for cleaning surfaces, such as heating surfaces, which impactor comprises 5 and a dumbbell (1), a hammer piece (8) supported by the body (1) is arranged to be reciprocated between a first end position to a second end position and comprising a first end surface (102) and a second end surface (103) opposite to the first end surface, - a cleaning unit (7) arranged to receive the impact energy of the hammer piece (8) as the hammer piece strikes the abutment surface (107) of the cleaning unit, - drive means for moving the hammer piece (8) back and forth supported by the body (1) between the first end position, in which the second end surface (103) of the hammer piece is at a maximum distance (SI) from the abutment of the support unit (7). Surface (107), and the second end position in which the hammer piece strikes the support unit to provide impact energy to the hammer piece; - a spring (6) adapted to transmit impact energy from the hammer piece (8) to the cleaning unit (7), characterized in that - the body (1) comprises a first gas space (100) defining one And a second gas space (101) defining a return pressure chamber, the first end surface (102) of the hammer piece (8) abutting against the first gas space (100) and the second end space (103) of the hammer abutting against the second gas space (101), - the drive means for displacing the hammer piece (8) from it The first end position of the second end position comprises a pressurized gas source (104) arranged to pressurize a gas pressure accumulator (105), which is arranged to be charged via a first valve (109) with a gas pressure (P1) from the pressurized gas source (104) via gas. from a supply line (115), from which gas pressure accumulator gas is arranged to flow through a second valve (110) to the first gas space (100) thus; The force that the gas pressure (P2) in the first gas space directs to the hammer piece is greater than an opposite directed force that the gas pressure (P3) in the second gas space (101) directs to the hammer piece, which further comprises gas removal means for removing gas pressure from the the second gas compartment (101) where the hammer piece (8) is displaced against the support unit (7), which gas removal means comprises a gas removal line (106), 20185506 prh 15 -05-2019 - the drive means for displacing the hammer piece (8) from the second end position back to the first end position comprises adjusting means for gas pressure and force, for providing the force which the gas pressure (P3) in the second gas space is directed towards the hammer piece (8) is greater than an opposite direction. force directed by the gas pressure 5 (P2) in the first gas compartment (100) towards the hammer piece, whereby in the first gas space a gas removal channel (108) joins to dissipate gas from the first gas space when the hammer piece is displaced from the second end position to the first end position. . Stroke device according to claim 1, characterized in that The gas pressure and power metering devices comprise gas feeder means for supplying gas to the second gas compartment (101), such that the force as the gas pressure (P 3) in the second gas space directed towards the hammer piece (8) is greater than an opposite directed force which the gas pressure (P2) in the first gas space (100) is directed towards the hammer piece. The impact device according to claim 2, characterized in that the gas supply means are arranged to supply gas to the second gas space (101) via a third valve (111), and that the gas supply devices are arranged to receive gas pressure from the gas source (104). 4. Impact device according to claim 1, 2 or 3, characterized In that the hammer piece (8) is a piston-like element and that the body (1) of the impact device defines for the hammer piece (8) a cylindrical space which encloses the first gas space (100) and the second gas space (101). 5. Impact device according to claim 4, characterized in that the gas pressure accumulator (105) surrounds the cylindrical space. 25 Impact device according to claim 5, characterized in that the gas pressure accumulator (105) is a tubular space surrounding the cylindrical space. The impact device according to any preceding claim 3-6, characterized in that the third valve (111) is a quick-discharge valve connected to the gas removal line (106) and the pressurized gas source (104), the pressurized gas source (104) being arranged to displace the second gas space. (101) under a pressure (P3) greater than the gas pressure (P2) of the first gas chamber (100) to displace the hammer piece ( 8) from the second end position to the first end position. Stroke device according to claim 7, characterized in that it comprises a throttle check valve (114) which is arranged to delay the opening of the first valve (109), thus opening the quick discharge valve before the first valve opens. The impact device according to claim 6, characterized in that the gas removal line (106) is connected to a pressure reducing valve (112). The impact device of any preceding claim 2-9, characterized in that it comprises a fourth valve (113) connected to the supply line (115) and the gas removal line (106) for supplying gas from the pressurized gas source (104) selectively to the pressurized gas accumulator (105). via the feed line (115) or into the second gas space via the gas removal line (106). 10 The impact device according to claim 10, characterized in that the function of the impact device is arranged adjustably via a control unit (120) which controls the opening, closing and any adjustment of the fourth valve (113). Stroke device according to any preceding claim, characterized in that the cleaning unit (7) comprises a cleaning body (7a) and a cleaning part (7b) arranged to be displaced supported by the body (1), and that the spring (6) is arranged between the cleaning part (7b) and the cleaning body (7a).