阅读说明：本技术 空气在电池和电池隔室之间的狭槽中泄漏的手持电动作业工具 (Hand-held electric power tool with air leakage in slot between battery and battery compartment ) 是由 托博约恩·阿尔姆奎斯特 保罗·约翰松 弗雷德里克·卡尔松 于 2020-11-25 设计创作，主要内容包括：一种手持电动切断工具(100,200,800,1000,1900,2300),包括风扇(145)和电池隔室(150),该风扇布置成由电动机(140)驱动以产生冷却气流(160),该电池隔室包括布置成向电动机(140)供电的电存储装置(220,1800),例如电池,其中,冷却空气管道布置成将冷却气流(160)朝向形成在电池隔室(150)的壁中的出口孔(1750)引导,其中出口孔(1750)面对形成在电存储装置(220,1800)的外壳中的对应的入口孔(1870),以用于接收冷却空气,从而在电存储装置(220,1800)中产生高于大气压力的空气压力,其中,第一狭槽段(Ss1)由出口孔(1750)和入口孔(1870)之间的距离形成,使得冷却气流(160)的第一部分(2415)经由第一狭槽段(Ss1)泄漏到切断工具的外部。(A hand-held power shut-off tool (100, 200, 800, 1000, 1900, 2300) comprising a fan (145) arranged to be driven by an electric motor (140) to generate a cooling air flow (160) and a battery compartment (150) comprising an electrical storage device (220, 1800) arranged to supply power to the electric motor (140), such as a battery, wherein a cooling air duct is arranged to direct the cooling air flow (160) towards an outlet aperture (1750) formed in a wall of the battery compartment (150), wherein the outlet aperture (1750) faces a corresponding inlet aperture (1870) formed in a housing of the electrical storage device (220, 1800) for receiving cooling air to generate an air pressure in the electrical storage device (220, 1800) that is above atmospheric pressure, wherein a first slot segment (Ss1) is formed by a distance between the outlet aperture (1750) and the inlet aperture (1870) such that a first portion (2415) of the cooling air flow (160) leaks to the shut-off tool via a first slot segment (Ss1) An exterior of the tool.)

1. A hand held power tool cutter (100, 200, 800, 1000, 1900, 2300) comprising a fan (145) arranged to be driven by an electric motor (140) to generate a cooling air flow (160) and a battery compartment (150) comprising an electrical storage device (220, 1800), such as a battery, arranged to power the electric motor (140), wherein a cooling air duct is arranged to direct the cooling air flow (160) towards an outlet aperture (1750) formed in a wall of the battery compartment (150), wherein the outlet aperture (1750) faces a corresponding inlet aperture (1870) formed in a housing of the electrical storage device (220, 1800) for receiving cooling air to generate an air pressure above atmospheric pressure in the electrical storage device (220, 1800), wherein a first slot segment (Ss1) is formed by the distance between the outlet aperture (1750) and the inlet aperture (1870), causing a first portion (2415) of the cooling airflow (160) to leak outside of the hand-held power shut-off tool via the first slot segment (Ss 1).

2. The hand-held power cut-off tool (100, 200, 800, 1000, 1900, 2300) of claim 1, wherein a distance between the electrical storage device (220, 1800) and the wall of the battery compartment (150) is between 0.5mm and 2.0mm, preferably about 1.0 mm.

3. The hand-held powered severance tool (100, 200, 800, 1000, 1900, 2300) of claim 1 or 2 wherein the electrical storage device (220, 1800) comprises one or more electrical connectors (1840) arranged to mate with corresponding contact strips (1740) arranged in the battery compartment (150), wherein an opening in the housing of the electrical storage device (220, 1800) is formed to connect with the electrical connectors (1840) such that a second portion (2425) of the cooling airflow leaks out of the hand-held powered severance tool through the opening and via a second slot segment (Ss2) formed between the electrical storage device (220, 1800) and the wall of the battery compartment (150).

4. The hand-held powered severance tool (100, 200, 800, 1000, 1900, 2300) of any of claims 1-3 wherein an air outlet (1860) is formed in a housing of the electrical storage device opposite the inlet aperture (1870) to form a channel for cooling air to flow through the electrical storage device, wherein a third slot segment (Ss3) is formed by a distance between the air outlet (1860) and the wall of the battery compartment (150) such that a third portion (2435) of the cooling airflow (160) leaks outside of the hand-held powered severance tool via the third slot segment (Ss 3).

5. The hand-held power severance tool (100, 200, 800, 1000, 1900, 2300) according to any of the preceding claims,

wherein a cooling air duct is arranged to direct a portion of the cooling air flow (160) from the first portion (110) and into the second portion (120) to cool the electrical storage device.

6. The hand-held powered severance tool (100, 200, 800, 1000, 1900, 2300) according to any preceding claim wherein the first portion (110) is vibrationally isolated from the second portion (120) by one or more resilient elements (210).

7. The hand-held electric power cutoff tool (100, 200, 800, 1000, 1900, 2300) of any one of the preceding claims, wherein a portion of the cooling airflow (160) that enters from the first portion (110) into the second portion (120) is arranged to pass through a control unit of the hand-held work tool (100).

8. The hand-held power cut-off tool (100, 200, 800, 1000, 1900, 2300) of any one of the preceding claims, wherein a portion of the cooling airflow (160) directed from the first portion (110) into the second portion (120) passes via a bellows or other flexible airflow conduit (170) arranged between the first portion (110) and the second portion (120).

Technical Field

The present disclosure relates to an electric hand-held working apparatus, such as a cutting tool and a saw for cutting concrete and stone.

Background

Hand-held power tools for cutting and/or grinding hard materials, such as concrete and stone, include powerful motors to provide the power required for handling the hard materials. These motors generate a large amount of heat and therefore need to be cooled to prevent overheating. The electric work tool generates heat by the electric motor and by the battery and control electronics. There is a need for an efficient method for cooling such a work tool.

Work tools also typically produce vibrations that may be harmful or at least cause discomfort to the operator of the tool. It is desirable to protect the operator from prolonged exposure to intense vibration.

The environment in which these types of tools are used is often harsh. The work tool is exposed to water, dust, debris, and mud, which may adversely affect tool performance. For example, mud may accumulate inside the work tool where it eventually causes the tool to fail. It is desirable to prevent the accumulation of dust and mud inside the work tool.

Ease of operation is particularly important for work tools used on construction sites. For electric work tools, it is desirable to enable field battery replacement in an efficient and convenient manner, wherein the battery is easily inserted into the work tool, wherein the battery is snugly held in the work tool, and wherein the battery is easily released from the work tool.

In summary, there are challenges associated with handheld work tools.

Disclosure of Invention

It is an object of the present disclosure to provide an improved handheld work tool that solves the above mentioned problems.

This object is at least partly achieved by a hand-held power cut-off tool comprising a fan arranged to be driven by an electric motor to generate a cooling air flow, and a battery compartment comprising an electrical storage device, such as a battery, arranged to supply power to the electric motor. The cooling air duct is arranged to direct a cooling air flow towards an outlet aperture formed in a wall of the battery compartment, wherein the outlet aperture faces a corresponding inlet aperture formed in a housing of the electrical storage device for receiving cooling air to generate an air pressure in the electrical storage device above atmospheric pressure. The first slot segment is formed by the distance between the outlet aperture and the inlet aperture such that a first portion of the cooling air flow leaks to the outside of the shut-off tool via the first slot segment.

This first portion of the cooling air flow leaking through the slot must be overcome by dirt, dust and mud in order to enter and contaminate the battery compartment. Thus, the battery compartment remains clean, which is advantageous as it simplifies the insertion and removal of the electrical storage device.

As set forth in the dependent claims, it is also possible to generate additional slot sections with a cooling air flow which keeps the slot sections free of dirt, dust and mud.

Further advantages are obtained by the features set forth in the dependent claims.

In general, all terms used in the claims are to be interpreted according to their ordinary meaning in the technical field, unless explicitly defined otherwise herein. All references to "a/an/the element, device, component, means, step, etc" are to be interpreted openly as referring to at least one instance of the element, device, component, means, step, etc., unless explicitly stated otherwise. The steps of any method disclosed herein do not have to be performed in the exact order disclosed, unless explicitly stated. Other features and advantages of the invention will become apparent when studying the appended claims and the following description. Those skilled in the art realize that different features of the present invention can be combined to create embodiments other than those described in the following, without departing from the scope of the present invention.

Drawings

The present disclosure will now be described in more detail with reference to the accompanying drawings, in which

FIG. 1 illustrates an example work tool;

2A-2C illustrate views of another example work tool;

3A-3B illustrate views of a work tool support arm;

fig. 4 to 6 show bellows for guiding the air flow;

fig. 7A to 7C schematically show a locking mechanism;

FIG. 8 illustrates an example work tool having a battery locking mechanism;

FIG. 9 schematically shows details of the battery locking mechanism;

10A-10C illustrate views of an example work tool;

FIG. 11 schematically illustrates a fan;

FIG. 12 illustrates an example fan for a work tool;

FIG. 13 illustrates an example fan housing;

figures 14A to 14C show details of the work tool support arm;

figure 15 shows a drive arrangement for driving a circular cutting tool;

FIG. 16A shows a rear handle segment with a water hose connection;

figures 16B to 16C show details of the water hose connector device;

fig. 17A to 17B show details of the battery compartment;

18A-18C illustrate a battery for insertion into a battery compartment;

FIG. 19 schematically illustrates a severing tool;

FIG. 20 shows a detail of the severing tool;

FIG. 21 illustrates an example damping member;

FIG. 22 illustrates another example damping member;

FIG. 23 illustrates cooling air flow through portions of a severing tool;

FIG. 24 schematically illustrates cooling air flow;

fig. 25 schematically shows a mass distribution of a work tool.

Detailed Description

The present invention now will be described more fully hereinafter with reference to the accompanying drawings, in which certain aspects of the invention are shown. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments and aspects set forth herein; rather, these embodiments are provided by way of example so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. Like numbers refer to like elements throughout.

It is to be understood that the present invention is not limited to the embodiments described herein and illustrated in the drawings; on the contrary, those skilled in the art will recognize that many variations and modifications are possible within the scope of the appended claims.

Fig. 1 shows a handheld work tool 100. The work tool 100 in fig. 1 includes a rotatable circular cutting tool 130, but the techniques disclosed herein may also be applied to other cutting tools, such as chainsaws, core drills, and the like. The motor 140 is arranged to drive the cutting tool. This motor is powered by an electrical energy storage device arranged to be held in the battery compartment 150.

The motor generates a large amount of heat during operation. To prevent the motor from overheating, the fan 145 is arranged to be driven by the motor 140. This fan may be attached to the motor shaft, for example, directly, or by some means of transmission. The fan creates an air flow that carries heat away from the motor, thereby cooling the motor.

The work tool 100 is arranged to be held by a front handle 190 and a rear handle 195, and operated by a trigger 196 in a known manner. Since excessive vibration may be uncomfortable for an operator using the work tool 100, it is desirable to minimize vibration in the handle and trigger. Excessive vibration may also reduce the life of tool components such as cable connections and electronics. To reduce these vibrations, the work tool 100 includes a first portion 110 and a second portion 120 arranged in vibrational isolation from each other. The first part 110 comprises an interface for holding a cutting tool 130 and further comprises a motor 140 arranged to drive the cutting tool. Thus, the first part comprises the main vibration generating element of the work tool.

Notably, second portion 120 includes handles 190, 195 and trigger 196, and is thus the portion that interacts with the operator of work tool 100. The second portion 120 also includes a battery compartment 150 for holding an electrical storage device, and control electronics for controlling various operations of the work tool 100.

Since the vibrations generated in the first part 110 are not transferred, or at least not transferred in a significant amount, to the second part 120, the operator of the device 100 will not be subjected to vibrations, which is advantageous since he or she may be able to work for a longer period of time in more comfortable working conditions.

The vibration is usually in m/s²Is a unit measurement, and it is desirable to limit tool vibration in the front and rear handles to 2.5m/s²The following. In "vibrators-Swedish working environment administration about vibrationsThe tool vibrations, guidelines for limiting tool vibrations and the measurement of tool vibrations are discussed in the general recommendations for dynamic regulations and related regulatory applications (the swedish work environment administration, AFS 2005: 15).

According to some aspects, the work tool 100 comprises a first part 110 and a second part 120, which are arranged in vibration isolation from each other by a vibration isolation system arranged to limit front and rear handle vibrations to below 2.5m/s²The value of (c).

The cooling air duct is arranged to direct a portion of the cooling air flow 160 from the first portion 110 into the second portion 120 for cooling the electrical storage device. This means that the fan 145 is used to cool both the motor 140 and the source of electrical energy, which is an advantage since only a single fan is required.

Here, the duct is a channel arranged to guide a flow such as a gas flow. The cooling air duct may be formed as part of the inner space enclosed by the work tool body part, or as a hose for other types of ducts, or as a combination of different types of ducts.

Any control electronics included in the second portion 120 may also be arranged to be cooled by the portion of the cooling airflow 160 directed from the first portion 110 and into the second portion 120. Fig. 1 schematically shows a cooling flange 180 associated with such control electronics, which cooling flange 180 is optional, i.e. this part of the cooling air flow can be used to directly cool the control unit, which in this case constitutes the cooling flange. Thus, optionally, the portion of the cooling air flow 160 that enters the second portion 120 from the first portion 110 is arranged to pass through a cooling flange 180 associated with the control unit of the handheld work tool 100.

At least in part because the first and second portions are arranged in vibrational isolation from one another, effectively directing the portion of the air 160 from the first portion and into the second portion can be a challenge. Aspects of the disclosed work tool address this challenge by providing a bellows or some other type of flexible airflow duct between the first and second portions to direct that portion of air from the fan 145 toward the battery compartment 150. These bellows 170 will be discussed in more detail below in conjunction with fig. 4-6. Corrugated tubes are sometimes also referred to as flexible covers, crimped structures, corrugated structures or machine direction covers. A hose formed of a flexible material may be used instead of the bellows.

In summary, fig. 1 schematically shows a handheld work tool 100 comprising a first part 110 and a second part 120 arranged in vibration isolation from each other. According to some aspects, the first portion 110 is vibrationally isolated from the second portion 120 by one or more resilient elements.

The hand-held work tool may be a cutting tool as shown in fig. 1, but it may also be a chain saw or other work tool for cutting hard materials. The first part comprises an interface for holding the cutting tool 130 and a motor 140 arranged to drive the cutting tool. The drive means may for example comprise a belt drive or a combination of a belt drive and a gear transmission. The motor 140 is arranged to drive a fan 145 configured to generate a cooling air flow for cooling the motor 140. The fan may for example be directly connected to the motor shaft, or it may be indirectly connected to the motor shaft via some kind of transmission or drive, such as a belt drive or a gear drive.

The second part 120 comprises a battery compartment 150 for holding an electrical storage device arranged to supply power to the electric motor 140, and the cooling air duct is arranged to direct a portion of the cooling air flow 160 from the first part 110 and into the second part 120 to cool the electrical storage device. The source of electrical energy may be a battery, or some type of fuel cell, or the like.

Fig. 2A-2C illustrate different views of an example handheld work tool 200 arranged to hold a cutting tool through a cutting tool interface 260. The resilient element separating the first part 110 from the second part 120 is here a compression spring 210. However, as mentioned above, some type of resilient material member, such as a rubber bushing, may also be used as an alternative to or in combination with the spring. Leaf springs may also be an option for vibrationally isolating the first portion 110 from the second portion 120.

Fig. 2B shows a holder 270 for an additional blade bushing. The cutting discs may have different sizes when they reach the central hole in the blade. Some of the blade holes are 20mm wide, while some others are 25.5mm wide. There are even some markets where a 30.5mm center hole of the blade is common. To allow for the use of different types of blades having different sizes on the central blade bore, the handheld work tool 200 includes a retainer 270 disposed on the work tool body for retaining the blade bushing. This additional blade bushing preferably has a different size than the blade bushing mounted in connection with cutting tool interface 260.

Fig. 2A shows an example electrical storage device 220 (here a battery) assembled in the battery compartment 150. This battery may be held in place by a battery locking mechanism, which will be discussed in more detail below in conjunction with fig. 7A-7C, 8, and 9. Other types of electrical energy sources that may be used with the devices and techniques disclosed herein include, for example, fuel cells, supercapacitors, and the like.

According to some aspects, the cooling air flow for cooling the motor 140 extends through the handheld work tool transversely 230, 245, 201 with respect to the plane of extension of the circular cutting tool 130. Here, with reference to fig. 2C, the lateral direction should be interpreted relative to the extension direction 202 in which the work tool extends from the rear handle 195 towards the cutting tool and relative to the extension plane of the cutting tool 130 (which is more or less vertical in fig. 2C). Air from the environment is drawn into the work tool interior via the air inlet 230 on one side of the tool and is at least partially pushed out of the work tool interior via the first air outlet 245 on the other side of the tool, which is formed in a direction transverse to the air inlet 230.

A portion of the air flow drawn into the work tool via the air inlet 230 is guided via the air duct into the second portion 120, where it is used to cool the electrical storage device and optionally also portions of the electrical control circuitry. For example, referring to fig. 2B, this portion of the airflow is directed downward from the fan and then rearward in the tool toward the battery compartment 150 before exiting the work tool via the second air outlet 250 formed in the second portion 120 of the tool.

It should be understood that if the fan is running in reverse, the airflow may also be directed in the opposite direction. That is, the air outlets 245, 250 may also be used to draw cool air from the environment into the work tool 100, 200, and the air inlet 230 may be repurposed to instead allow hot air to exit the work tool.

Referring to fig. 10A, a portion of the airflow 160 directed downward from the fan and then rearward in the tool also exits the work tool via a third air outlet 251 formed inside the battery compartment 151. This third outlet is mainly arranged to cool the batteries contained in the battery compartment 150.

Fig. 3A and 3B illustrate some aspects of the disclosed work tool, wherein the first portion 110 includes a thermally conductive support arm 240 arranged to support the circular cutting tool 130 on a first end 241 of the support arm and to support the motor 140 at a second end 242 of the support arm opposite the first end 241 by a support surface 330. The motor 140 is then arranged to drive the cutting tool by some type of drive means, such as a belt drive or a combination of a belt drive and a gear transmission. The belt is not shown in fig. 3A, only the pulleys are shown. The support surface 330 presents a relatively large interface area between the motor 140 and the support arm 240, which allows for a large amount of heat transfer from the motor into the support arm material, at least in the case where the motor includes a corresponding surface for interfacing with the support surface. This heat is then dissipated from one or more cooling flanges 320 formed on the support arm 240. Thus, the support arm 240 includes one or more cooling flanges 320 arranged to dissipate heat away from the motor 140 via the support surface 330.

The support arm 240 is an arm of a severing tool, which may be equivalently referred to as the severing arm 240.

This heat transfer arrangement improves heat dissipation from the motor since the cooling air flow is more efficiently used to carry heat away from the motor.

The higher the thermal conductivity of the support arm, the more efficient the heat dissipation. According to some aspects, at least some portions of the support arm are formed from a material having thermal conductivity properties of 100 watts per meter kelvin (W/mK) or greater. For example, at least some portions of the support arm can be formed of aluminum, which has a thermal conductivity of about 237W/mK. Iron or steel is another option to provide the desired thermal conductivity. The support arms may also be formed of different materials, i.e., one highly thermally conductive material, such as copper, magnesium or aluminum, may be used to cool the flange, and another material, such as cast iron or steel, may be used to provide general structural support.

Fig. 14A-14C and 15 show details of an example support arm 240 arranged to support the circular cutter 130 on a first end 241 of the support arm and to support the motor 140 at a second end 242 of the support arm opposite the first end 241 by means of a support surface 330. Fig. 14A shows a view of the support arm 240 and the interior space 340 described above. Fig. 14B shows a first cross-sectional view along line a-a, and fig. 14C shows a second cross-sectional view along line B-B. The motor 140 includes a motor shaft that extends through a motor housing 141 in a known manner.

The first end 142 of the shaft is arranged to hold a pulley for driving the circular cutting tool 130. Fig. 15 shows a view of the support arm 240 with the drive pulley and drive belt in place to drive the circular cutting tool 130.

The second end 143 of the motor shaft is arranged to drive a fan 145. The example fan 145 shown in FIG. 14B is a conventional axial fan. Another more advanced example of the fan 145 will be discussed below in conjunction with fig. 11-13.

Optionally, the support arm 240 is arranged to at least partially surround the motor 140, thereby protecting the motor and increasing the cooling efficiency of the air flow 1330 through the motor. To this end, the support arm 240 comprises a cup-shaped recess, as seen in detail in fig. 10C, wherein a support surface 330 constitutes the bottom of the recess, and a cylindrical wall 350 extends from the periphery of the support surface 330 to surround the motor housing 141 of the motor 140 when the motor is supported on the support surface 330. The motor 140 is arranged to be firmly bolted to the support surface 330 by means of the bolt holes 335, thereby ensuring good thermal conduction and mechanical integrity between the motor 140 and the support arm 240. A slot is formed between the cylindrical wall 350 and the motor 140, i.e. the recess wall 350 is radially spaced from the motor housing. This slot is arranged to direct a cooling air flow 1330 from the fan 145 through the motor 140. An air flow 1330 extends from the fan 145 transversely through the support arm 240 to cool the motor 140. The cooling air flow 1330 then passes through the opening 310 and into the interior space 340, and then exits via the first air outlet 245 shown in fig. 2B.

According to some aspects, at least 30% of the volume of the motor 140 (i.e., the volume of the motor including its housing 141) is surrounded by the support arm 240. This means that the cylindrical wall 350 extends a distance 144 from the support surface 330 to enclose at least 30% of the volume of the motor housing 141. Thus, the motor is optionally significantly embedded in the support arm, or even completely embedded as shown in fig. 14A-14C, thereby improving the structural integrity of the motor and support arm assembly and improving heat transfer away from the motor. Cooling of the motor 140 is also improved by the slots formed between the cylindrical wall and the motor housing, which cooperate with the thermally conductive support arms and the cooling flange to effectively cool the motor.

The support arm 240 and the motor 140 may also be at least partially integrally formed. This means that some components of the motor 140 may be shared with the support arm 240. For example, a portion of the support arm 240 may form a portion of a motor housing, such as a motor cover facing the support arm. Common components shared between the support arm 240 and the motor 140 may be machined or molded, for example. Also, optionally, the motor shaft may abut a surface of the support arm to improve mechanical integrity.

It should be noted that the features of the at least partially integrally formed support arm and motor may be advantageously combined with, but not dependent on, any of the other features disclosed herein. Accordingly, disclosed herein is a support arm 240 and motor 140 assembly for a work tool 100, wherein the support arm and motor are at least partially integrally formed.

Referring to fig. 2B, the first portion 110 optionally includes a shroud 115 configured to enclose an interior space 340. As mentioned above, a portion of the cooling air flow is arranged to be directed into the interior space 340, thereby increasing the air pressure in the interior space 340 of the shrouded 115 above the ambient air pressure level. The interior space 340 is bounded on one side by a support arm (discussed below in connection with fig. 3A and 3B) and on the other side by the belt cover 115, which assumes the function of a cover that is configured to engage the support arm to protect the drive belt therein. The belt hood 115 includes an air outlet 245 through which the cooling air stream exits the interior space. This air outlet 245 is configured to have an area such that the air pressure in the interior space 340 of the shrouded 115 is increased above the ambient air pressure level by a desired amount.

An increase in air pressure in the interior space 340 means that the air flow will exit through all openings in the interior space 340, i.e. any cracks or the like, and not just the air outlet 245. This in turn means that water, dust, debris and mud will have to overcome this airflow in order to enter the interior. Thus, accumulation of undesirable material within the work tool is reduced.

The water in the interior space 340 may cause the drive belt to slip and is therefore undesirable. An increase in air pressure in the interior space 340 of the belt guard 115 means that less water can enter the interior space, which is an advantage. Thus, the requirements for the belt may be reduced, such that for example a belt with a smaller number of ribs may be used.

As described above, the portion of the cooling airflow 160 directed from the first portion 110 and into the second portion 120 may pass via a bellows or other flexible airflow conduit 170 disposed between the first portion 110 and the second portion 120. An example of such a bellows 10 is shown in detail in fig. 4.

According to some aspects, the shore durometer value or shore hardness associated with the bellows 170 is between 10-70, preferably between 50-60, as measured with a type a durometer according to DIN ISO 7619-1.

The bellows 170 optionally includes error proofing features 410, 420. This error-proofing feature comprises at least one protrusion 410, 420 configured to enter a corresponding recess formed in the first part 110 and/or in the second part 120, thereby preventing erroneous assembly of the bellows with the first part 110 and the second part 120.

The bellows 170 also optionally includes at least one edge portion 430, 440 of increased thickness. Each such edge portion is arranged to enter a corresponding groove formed in the first part 110 or in the second part 120, thereby fixing the bellows 170 with respect to the first part or the second part, similar to a sail edge (sail leech) fitted into a mast (mast). Fig. 5 and 6 schematically show the bellows assembled to the first and second parts, respectively, by the edge portion.

The bellows shown in fig. 4 is arranged to have a symmetrical shape with respect to a symmetry plane 450, which is parallel to the extension direction of the edge portions 430, 440. Thus, advantageously, the bellows can be assembled with the first and second parts regardless of which side of the bellows is facing upwards. That is, the bellows may be rotated 180 degrees about the axis of symmetry 460 and assembled with the first and second portions.

Fig. 7A-7C schematically illustrate aspects of the battery compartment 150, wherein the battery compartment includes a battery locking mechanism 700. The battery locking mechanism includes a locking member 710 rotatably supported on a shaft 720. The locking member comprises a leading edge portion 750 arranged to enter a recess 760 formed in the electrical energy source 220 to lock the electrical energy source in place, wherein the leading edge portion 750 has an arcuate shape with a curvature corresponding to the curvature of a circular section with a radius 740 corresponding to the distance from the leading edge portion 750 to the center of the shaft 720, and wherein the recess 760 formed in the electrical energy source 220 comprises a surface 770 arranged to engage the leading edge portion 750, wherein the surface 770 has an arcuate shape matching the arcuate shape of the leading edge portion 750.

Thus, when the source of electrical energy 220 is housed in the battery compartment 150, the locking member is inactive, simply yielding to the source of electrical energy as it enters the compartment. This stage of inserting the electrical energy source 220 into the compartment 150 by moving it in an insertion direction 701 is schematically illustrated in fig. 7A and 7B. The locking member 710 then swings into the recess 760 where it prevents the battery from retracting from the battery compartment. The locked position is shown in fig. 7C. Notably, the arcuate shape of the leading edge portion 750 allows the locking mechanism to rotate out of the locked position with less resistance even if there is some friction between the leading edge portion 750 and the surface 770 disposed to engage the leading edge portion 750.

The locking member may be arranged to be spring biased towards the locking position and may be operated by a lever or button mechanism, as discussed below in connection with fig. 8 and 9.

It should be understood that there may be any number of locking members arranged in the battery compartment in the manner described above, i.e. any position from a single locking member to a plurality of locking members.

According to some aspects, the battery compartment 150 comprises at least one resilient member 780 arranged to urge the source of electrical energy into the locked position, i.e. in a direction opposite to the insertion direction 701. When compressed by a source of electrical energy, the resilient member 780 pushes on the source of electrical energy to repel it from the battery compartment 150. This pushing force increases the contact pressure between the leading edge portion 750 and the surface 770 disposed to engage the leading edge portion 750, thereby improving the retention of the source of electrical energy.

According to one example, a user inserts a battery into the battery compartment in an insertion direction. When the battery is fully inserted, it contacts the resilient member 780 and the locking member 710 enters a recess 760 formed in the electrical energy source 220 to lock the electrical energy source in place. When compressed by the battery, the elastic member is pushed back in a direction opposite to the insertion direction. This pushing force from the resilient member increases the contact force between the leading edge portion 750 of the locking member and the surface 770 arranged to engage the leading edge portion 750 to more securely hold the battery in place.

The resilient member 780 optionally comprises any of a resilient material member, a compression spring, and/or a leaf spring.

When the electrical energy source is released by the locking mechanism 700, the resilient member 780 will also eject the electrical energy source 220 a short distance from the battery compartment 150. Thus, when the button mechanism 810 is operated to release the battery, the battery is ejected from the battery compartment 150, making it easier to grasp the battery and pull it out of the battery compartment.

Fig. 7C schematically shows an example of such an elastic member 780. The resilient member urges the electrical energy source in direction 702, but is prevented from moving in this direction by the locking member 710 engaging the recess 760. The arrangement of the resilient member 780 and the locking member 710 on opposite sides S1, S2 of the electrical energy source 220 creates a twisting motion 795 or rotational torque, which further increases the holding effect by increasing the friction between the battery and the battery compartment walls in a manner similar to a stuck cabinet or desk drawer. This further increase in retention reduces vibration of the battery because the battery is now more snugly retained in the battery compartment.

Fig. 8 illustrates an example work tool 800 that includes a battery locking mechanism 700. The locking member 710 is rotatably supported on a shaft 720 wherein it is allowed to rotate about a rotational axis 820. An operator may use the button mechanism 810 to rotate the locking member 710 so that it clears the recess, allowing the battery to be removed in direction 702.

According to some aspects, the locking member 710 is spring biased toward the locked position. Thus, when the electrical energy source 220 is inserted into the recess 150, the locking member 710 snaps into the locked position. The button mechanism 810 may overcome the spring bias when the electrical energy source is to be removed from the battery compartment.

Fig. 9 shows details of a battery locking mechanism 700 for the battery compartment 150. Such battery locking mechanisms may be used with many different types of tools (i.e., grinding tools, grinders, chain saws, drills, cutting tools, etc.). Accordingly, the battery locking mechanism disclosed herein is not limited to use with the severing tool discussed above in connection with fig. 1-8.

The battery locking mechanism 700 shown in fig. 9 includes a locking member 710 that is rotatably supported on a shaft 720 as described above and that is optionally spring biased to a locked position. The locking member comprises a leading edge portion 750 arranged to enter a recess 760 formed in the electrical energy source 220 to lock the electrical energy source in position, as discussed above in connection with fig. 7A-7C. The leading edge portion 750 may have an arcuate shape with a curvature corresponding to the curvature of a circular segment having a radius 740 corresponding to the distance from the leading edge portion 750 to the center of the shaft 720. The recess 760 formed in the electrical energy source 220 comprises a surface 770 arranged to engage the leading edge portion 750. This surface 770 has an arcuate shape that matches the arcuate shape of the leading edge portion 750. Notably, the battery locking mechanism 700 shown in fig. 9 includes two locking members 710 separated by a distance. This double arrangement of the locking members increases the robustness of the locking mechanism 700.

Thus, as explained in connection with fig. 7A to 7C, an electrical energy source, such as a battery, may be inserted into the battery compartment, i.e. into the compartment 150 shown in fig. 9, in the insertion direction 701. At a certain moment, the locking member can enter the locking position, i.e. it enters the recess 760. In this position, the battery is prevented from moving in a direction 702 opposite to the insertion direction 701. However, it may make some click and may not be firmly fixed. To improve the battery locking mechanism, and to better hold the source of electrical energy in place, one or more resilient members 780 (e.g., compression springs or rubber bushings) are disposed in the battery compartment 150 and/or on the source of electrical energy to urge the source of electrical energy when it is fully inserted into the compartment. The thrust increases the contact force between the leading edge portion 750 and the surface 770 configured to engage the leading edge portion. This increased contact force increases friction to better hold the source of electrical energy in place.

According to some aspects, the at least one resilient member 780 and the battery locking mechanism 700 are arranged at opposite sides S1, S2 of the battery compartment 150, i.e. there is a plane 910 dividing the battery compartment into two parts, wherein the resilient member 780 is comprised in one part and the battery locking mechanism is comprised in the other part. This means that one or more resilient members push on the battery source from one direction to cause a twisting motion 795 or torque. This twisting motion can be contrasted with a drawer that is jammed in a cabinet or desk. Thus, the electrical energy source is prevented from rattling and is more securely held in the battery compartment 150.

Fig. 10A and 10B illustrate an example work tool 1000 that includes a particular type of fan 145. This fan comprises a member, preferably but not necessarily disc-shaped, which is arranged on the shaft of the motor 140, which shaft also constitutes the rotational axis of the fan. The member extends in a plane perpendicular to the axis of rotation and comprises two different types of fan sections. The first part acts as an axial fan and pushes cooling air laterally 201 through the work tool 1000 to cool the motor 140. The second part of the fan functions as a radial fan, also called centrifugal fan, to push cooling air down and into the second part of the work tool in cooperation with a fan scroll (scroll) fitted to the radial fan part. The fan 145 is shown schematically in fig. 11, and one example of a fan is shown in fig. 12, where the direction of rotation 1130 and the axis of rotation 1140 have been indicated. Fig. 11 also indicates a direction 1145 referred to as "radially outward" from the axis of rotation 1140.

Fig. 10A illustrates an example tool in which, according to some aspects, a portion of the cooling air flow 160 from the first portion 110 and into the second portion 120 is arranged to enter the electrical energy source 220 via a third outlet 251 arranged inside the battery compartment 150. This connection to the source of electrical energy improves the cooling efficiency by better cooling of the batteries, for example, in the battery.

The fan 145 includes: an axial fan section 1110 disposed peripherally on the fan 145, i.e., circumferentially along the fan disk-like boundary as shown in fig. 11 and 12; and a radial fan section 1120 that is centrally disposed on the fan 145, i.e., radially inward from the axial fan section as shown in fig. 11 and 12. Thus, the axial fan portions are arranged radially outward 1145 from the axis of rotation 1140 in the plane of extension. The axial fan section 1110 is arranged to generate a cooling air flow 1330 for cooling the electric motor 140, and the radial fan section 1120 is arranged to generate a portion of the cooling air flow 160 from the first section 110 and into the second section 120 for cooling the electrical storage device.

Axial fans or axial fans have blades that force air to move parallel to a shaft about which the blades rotate, i.e., the axis of rotation. Fans of this type are used in a variety of applications, from small cooling fans for electronics to large fans for use in wind tunnels. Axial fans are particularly suitable for generating a large air flow in the ducts of the linear circuit, which is the case when cooling the motor 140.

Radial or centrifugal fans use centrifugal power provided by the rotation of the impeller to increase the kinetic energy of the air/gas. As the impeller rotates, gas particles near the impeller are thrown off the impeller and then move into the fan housing wall. The gas is then directed through a fan scroll to an outlet. The radial fan pushes cooling air under pressure through the air duct with bends and narrow channels better than the axial fan, which is the case when the air duct enters the second section and faces the battery compartment 150.

According to some aspects, the axial fan and the radial fan are formed as separate components mounted on the same motor shaft.

The radius of the radial fan may correspond to the radius of the motor cover.

The relationship between the radius of the radial fan and the radius of the fan may be on the order of 50% -70%.

Thus, advantageously, the fan shown in fig. 10 to 13 provides efficient motor cooling and efficient cooling of the tool components (e.g. the control unit and the electrical energy source) in the second part. This is achieved by providing two different types of fans on a single fan member.

Fig. 10C shows a more detailed view of a portion of the support arm that includes one or more cooling flanges 320 arranged to dissipate heat from the motor 140 via the support surface 330. The above-described opening 310 for allowing air to enter the interior space 340 can also be seen. The axial fan section 1110 forces air through the motor and through the holes, thereby cooling the motor 140.

The fan 145 may optionally be assembled in a fan housing 1010 illustrated in fig. 13. The fan housing includes at least one opening 1310 disposed circumferentially radially outward from the axis of rotation 1140 to receive a cooling air flow 1330 from the axial fan section 1110 for cooling the motor 140. The fan housing further includes a fan scroll 1320 centrally disposed in the housing to interface with the radial fan portion 1120 for directing a portion of the cooling airflow 160 from the first portion 110 into the second portion 120 to cool the electrical storage device.

Fig. 13 also shows a groove 1340 and a recess 1350 for receiving the bellows 170 having the edge portion 430 and the error-proofing feature 410 shown in fig. 4.

The fans discussed in connection with fig. 10A, 10B, 11, 12, and 13 are not only suitable for use with the types of work tools disclosed herein. Rather, such a fan may be advantageously used in any type of work tool where a first cooling airflow and a second cooling airflow are desired. Accordingly, a fan 145 for a handheld work tool 100, 200, 800, 1000 is disclosed herein. The fan 145 extends in a plane perpendicular to the axis of rotation of the fan 1140. The fan 145 comprises an axial fan section 1110 arranged radially outward from a radial fan section 1120 arranged centrally on the fan 145 with respect to the rotational axis 1140, wherein the axial fan section 1110 is arranged to generate a first cooling air flow for cooling a first handheld work tool component, and wherein the radial fan section 1120 is arranged to generate a second cooling air flow 160 for cooling a second handheld work tool component.

Optionally, axial fan section 1110 has an annular shape centered on rotational axis 1140, and wherein radial fan section 1120 has a disk-like shape centered on rotational axis 1140.

Also disclosed herein is a handheld work tool 1000 that includes the fan discussed in conjunction with fig. 10-13 and includes a fan housing 1010. The fan 145 is assembled in a fan housing 1010 comprising at least one opening 1310 arranged peripherally in the fan housing and radially outwardly from a rotational axis 1140 of the fan 145 for receiving a first cooling air flow from the axial fan section 1110 for cooling the first hand held work tool component, and a fan scroll 1320 arranged centrally in the fan housing for connecting with the radial fan section for directing a second cooling air flow 160 for cooling the second hand held work tool component.

Fig. 16A shows details of an alternative connector device 1600 for a water hose, preferably mounted near the rear handle 195, where it is easily accessible to an operator for attaching and detaching the water hose. The connector device 1600 includes a water hose connector component 1610, here shown as a fitting for a water hose quick connector system, i.e., a connector male component, that faces rearwardly away from the circular cutting tool 130. The connector fitting 1610 is fixedly mounted to the machine housing by a bracket 1620 such that the water hose connector component 1610 is fixedly held relative to the work tool. Alternatively, the female hose connector part may be fixedly mounted on the work tool by a similar bracket to obtain the same technical effects and advantages. The water hose 1630 extends away from the connector component 1610 toward the cutting tool 130. The water hose 1630 is arranged to be at least partially embedded in the tool housing in order to protect the water hose from damage during use of the tool 100.

Known water hose connector arrangements typically comprise a hose section between a bracket and a connector part (male or female connector part) on the work tool, which means that it is difficult to connect and disconnect the water hose with one hand. However, since the connector fitting 1610 is fixedly mounted on the machine housing by the bracket 1620, the connector arrangement 1600 allows for attachment and detachment of a water hose for supplying water to the cutting tool 130 with one hand during operation. Thus, the connector part is firmly supported by the machine housing where it is easily accessible and does not move around. For example, the operator may hold the tool with one hand via the front handle 190 and connect a water hose with the other hand. The connector component 1610 may be adapted to connect with any quick connector system on the market, for exampleA water hose system.

The water hose connector device 1600, including connector component 1610 and cradle 1620, may be implemented on any power tool requiring a supply of water, which is not limited to the particular tool discussed herein.

Fig. 16B and 16C show views of the connector device 1600 in more detail. Fig. 16B is a view corresponding to fig. 16A, while fig. 16C shows the connector device 1600 from an opposite viewpoint. Connector component 1610 and carrier 1620 are preferably integrally formed, i.e., machined or molded, from a single piece of material, such as a single piece of plastic or metal. An internal fitting 1640 for attaching the water hose 1630 may be arranged opposite the connector component 1610 to facilitate assembly of the connector device on the handheld work tool.

Fig. 17A and 17B show details of an example battery compartment 150. An electrical energy source, such as a battery, may be inserted into the battery compartment in the insertion direction 701, i.e. also into the compartment 150 as shown in fig. 9. Fig. 17A is a view opposite to the insertion direction 701, and fig. 17B is a view looking into the compartment 150 in the insertion direction 701. The locking member 710 discussed above in connection with, for example, fig. 9, can be seen in fig. 17A and 17B. The battery, which will be discussed in more detail below in connection with fig. 18A-18C, optionally includes a rear surface formed as a handle to simplify insertion and removal of the battery in the battery compartment 150.

Batteries used to power heavy duty cutting tools, such as the work tools discussed herein, are typically quite heavy. Therefore, the batteries must be held in the battery compartment 150 in a robust and reliable manner. To this end, the battery compartment 150 comprises a battery holding mechanism which is particularly suitable for supporting heavy batteries, i.e. weighing in the order of 5kg, for example between 3kg and 7 kg.

As described above, the battery compartment 150 extends transversely through the housing of the tool 100, 200, which defines a volume therein for receiving a battery. This volume is bounded by a rear wall Rw, which is positioned towards the rear handle 195 on the tool 100, and a front wall Fw, which is positioned towards the front of the tool 100, i.e. towards the cutting tool 130. The bottom surface Bs and the top surface Fs also define the volume. The example volume in fig. 17A and 17B is a rectangular shape with rounded corners.

The battery retention mechanism includes a support heel 1710 disposed on a mid-section of the side wall of the battery compartment, more specifically on the rear wall Rw closest to the rear handle 195. The heel 1710 is elongated with the direction of elongation extending transversely through the battery compartment, aligned with the direction of insertion of the battery in the battery compartment 150. When the machine rests on the ground support member 280, the support heel 1710 is parallel to the ground. Also, when the tool 100 is held in the normal operating position, the support heel is parallel to the ground and thus supports the battery against gravity. It is to be understood that the support heel 1710 may also be arranged on the front wall, i.e. on either of the front and/or rear wall of the battery compartment. The battery illustrated in fig. 18A to 18C and discussed below includes corresponding grooves that mate with the support heels.

According to some aspects, the support heel 1710 is metal-wrapped (hood) to increase mechanical integrity, i.e., the support heel 1710 is optionally constructed with an outer metal layer for increased mechanical strength.

According to some other aspects, the battery compartment further includes an upper groove 1720 and a lower groove 1730 for supporting the battery in the battery compartment 150. The grooves are arranged to cooperate with corresponding ridges on the battery such that the battery may be inserted into the battery compartment 150 in the insertion direction 701 at a position cooperating with the grooves. Thus, the support heel 1710 and the grooves 1720, 1730 together support the battery in the battery compartment in a safe and robust manner. The grooves 1720, 1730 have the function of guiding the battery when it is inserted into the battery compartment 150 and preventing snagging when the battery is removed from the battery compartment 150.

The grooves 1720, 1730 are preferably formed as dovetail grooves.

According to some aspects, the grooves 1720, 1730 are metal-wrapped for added mechanical strength, i.e., the grooves are reinforced with a liner layer of metal to add mechanical strength.

Fig. 17B also shows two resilient members 780 as discussed above in connection with fig. 7C, arranged to push the battery into a locked position, i.e. to push the electrical energy source in a direction opposite to the insertion direction 701.

A contact strip 1740 extending in the insertion direction 701 is arranged in the battery compartment 150 to mate with a corresponding electrical connector configured in a slot on the battery.

Also disclosed herein is a battery 1800 as shown in fig. 18A-18C for insertion into the battery compartment 150. The battery 1800 has a weight of between 3-7kg and comprises a groove 1810 arranged on one side of the battery to cooperate with a corresponding support heel 1710 arranged on the wall of the battery compartment 150. The groove optionally has an initial slope to simplify the fit with the support heel 1710. The battery 1800 also includes upper and lower ridges 1820, 1830 on opposite sides of the battery than the grooves 1810, as shown in fig. 18, for mating with corresponding grooves 1720, 1730 of the battery compartment 150. Thus, the battery 1800 is configured to be inserted into the battery compartment 150 discussed in connection with fig. 17A and 17B.

The grooves 1720, 1730 are preferably formed as dovetail grooves.

The battery 1800 includes at least one recess 760 configured to receive a corresponding locking member 710 of the battery locking mechanism 700 as described above. The locking member comprises a leading edge portion 750 having an arcuate shape and the recess 760 comprises a surface 770 arranged to engage the leading edge portion 750. The surface 770 has an arcuate shape that matches the arcuate shape of the leading edge portion 750. As shown in fig. 18A, two recesses are advantageously arranged on either side of the elongated support heel 1710.

The battery 1800 illustrated in fig. 18A-18C also includes one or more electrical connectors 1840 protectively disposed in slots extending in the insertion direction to mate with corresponding contact strips 1740 disposed in the battery compartment 150.

Optionally, the battery 1800 comprises a front surface F1 facing the insertion direction 701 when the battery 1800 is inserted into the battery compartment 150 and a rear surface F2 opposite the front surface, wherein the rear surface is formed as a handle 1850 to allow gripping by one hand.

The battery also includes electrical connectors 1840 configured in slots extending in the insertion direction to mate with corresponding contact strips 1740 disposed in the battery compartment 150. Thereby protecting the electrical connector from mechanical shock.

To facilitate cooling of the cells, as shown in fig. 18C, air inlets are disposed on the bottom side of the cells that are in fluid communication with air outlets 1860 disposed on the upper side of the cells. Thus, the airflow 160 from the fan 145 may be directed through the battery 1800 to better cool the battery cells.

The batteries and battery compartments discussed in connection with fig. 17 and 18 may also be used with other hand tools. Thus, the features disclosed in connection with the battery compartment and the battery are not dependent on any other particular features of the tool discussed herein.

Fig. 19 shows an example hand-held powered severance tool 1900 that includes a first portion 110 and a second portion 120 that are vibrationally isolated from one another by one or more damping members 170, 1910, optionally in combination with one or more resilient members (e.g., metal springs 210 shown in fig. 2A and 2C). As will be discussed in more detail below in connection with fig. 25, the first portion is associated with a first mass M1 and the second portion is associated with a second mass M2. Notably, the ratio of the second mass M2 to the sum of the masses M1+ M2 is much greater than, for example, the conventional values for a similarly sized engine powered cutoff tool. This mass ratio provides a more effective anti-vibration function between the first and second portions, as well as a more stable cutting operation, and also improves operator comfort during operation.

A problem that can potentially occur in handheld severing tools of the type discussed herein is that the cutting discs 130 become slightly oval during use. This is undesirable because an excessively elliptical cutting disk hinders cutting performance and may cause discomfort to the operator. Elliptical cutting disks may also be associated with an undesirable increased risk of kickback. An example of an elliptical cutting disk 130 is shown in insert 1920 of fig. 19. The elliptical cutting disks are associated with variations in the disk "diameter" D1, D2, measured on the disk, i.e., D1 and D2 in fig. 19 are not equal and differ by a non-negligible amount. The measurements D1 and D2 may be viewed as half the minor and major semi-axes of the ellipse, although it will be appreciated that elliptical cutting disks are not generally perfectly elliptical, but rather exhibit radial non-uniformity along their perimeter.

This problem with elliptical cutting disks tends to be more pronounced for lower cutting disk angular velocities ω, such as when the severing tool is operated at rotational speeds below about 3600-4000rpm, as measured at the axis of rotation of the cutting disk 130. Hand-held power severance tools that include vibration isolated first and second portions, such as the tools 100, 200, 800, 1000, 1900 discussed herein, may be particularly susceptible to the problems of elliptical cutting disks.

According to some aspects, the handheld power severance tool discussed herein, and in particular in connection with fig. 19-22, is arranged to operate at a cutting disc rotation speed ω below 4000rpm, and preferably about 3200 rpm.

A solution to the elliptical disc problem may be to simply increase the cutting disc rotation speed omega, for example, to speeds in excess of 4000 rpm. However, such high cutting disc speeds are undesirable for a number of reasons.

For example, when dry cutting, i.e., when cutting concrete or stone by a hand-held power cutoff tool without adding a fluid such as water to the cutting area, if the cutting disc speed is too high, it becomes difficult to effectively collect the generated dust, and therefore it is desirable to reduce the cutting disc speed in dry cutting applications. Suitable cutting disc speeds for dry cutting applications are typically on the order of about 3100-. These speeds may even be considered as maximum cutting speeds under normal dry cutting operating conditions.

A high cutting disc speed also means that the cutting disc stores more energy during operation. This in turn means that it becomes more difficult to rapidly reduce the cutting disc speed by braking, for example during a kickback event. Therefore, for safety reasons, it may be desirable to limit the cutting disc speed to a speed of approximately 3100-.

Furthermore, if the cutting disc speed is too high, the power severing tool may present challenges in generating sufficient torque to perform an effective cutting operation. For this reason, a cutting disc speed ω in the order of approximately 3100-.

It should be understood that the above-described cutting disc speeds are merely examples, which depend on many aspects, such as the type of tool, cutting disc size, motor specifications, etc. However, the general principles of high and low cutting disc speeds are applicable to most severing tools.

It has been realized that the problem of an oval cutting disc can be alleviated if a damping member is arranged between the first part 110 and the second part 120, optionally in combination with an elastic member formed as a metal spring for effective vibration isolation. These damping members differ from conventional spring-based anti-vibration units commonly used on tools of this type in that they are formed of an elastic material associated with a damping coefficient. The damping member dampens oscillatory behavior between two masses of a hand-held power cut-off tool that includes a first portion and a second portion arranged in vibration isolation from one another. By this inhibition, the tendency to form elliptical cutting blades at low cutting disc speeds is mitigated. This is at least in part because, without a damping member, the two masses of a debounce severing tool operating at a given cutting disk speed may enter into this oscillatory behavior to exert different cutting pressures on different portions of the cutting blade. That is, the oscillating motion may become synchronized with the rotation of the cutting disk. When a system comprising a first part 110 and a second part 120 enters this type of oscillation state, an elliptical cutting disc may be produced.

Modern internal combustion engine power cutters typically include resilient elements in the form of metal springs to dampen vibrations between the motor and the cutter disc components and the components with the handle. However, these springs are not damping members in the sense that the oscillatory behavior of one mass relative to the other is damped. The relative harmonic motion between two masses can be approximated by the behavior of the two masses connected by a spring, where the restoring force follows Hooke's Law and is proportional to the displacement of the two masses from an equilibrium position. Any system that is subject to simple harmonic motion is referred to as a simple harmonic oscillator. This type of oscillatory behavior can be mitigated by adding a damping effect to the system, which can be accomplished by adding a damping member associated with a damping coefficient (generally denoted c) or a device that limits the stroke length of one component relative to another. The damping ratio is a measure describing how quickly the oscillation decays from one "bounce" to the next. The damping ratio can vary from un-damped (ξ ═ 0), under-damped (ξ <1) through critical damped (ξ ═ 1) to over-damped (ξ > 1). The addition of a damping member to the mass-spring system has an effect on the damping ratio.

Referring also to fig. 1, fig. 19 shows a hand-held power severance tool 1900 that includes a first portion 110 and a second portion 120 arranged in vibration isolation from each other. The first portion 110 includes an arm 116 arranged to support a cutting disk 130 (shown in insert 1920 in fig. 19) and a motor 140 arranged to drive the cutting disk. The second part 120 comprises a front handle 190 and a rear handle 195 for operating the shut-off tool, and a battery compartment 150 for holding an electrical storage device 220, 1800 such as a battery arranged to supply power to the motor 140. An example of such a battery is discussed above in connection with fig. 18A-18C.

Notably, one or more damping members 170, 1910 are disposed between the first portion 110 and the second portion 120, wherein at least one damping member 170, 1910 is formed of an elastic material associated with a damping coefficient.

The one or more damping members are arranged to dampen or disturb oscillations of the second portion 120 relative to the first portion 110. Thus, the risk of ending up with an oval cutting disc is reduced.

According to aspects, the at least one damping member 170, 1910 is made of rubber, a resilient plastic material, a closed cell foam, or a resilient synthetic resin. Common to these damping elements is that they introduce a damping coefficient into the resonance equation of the mechanical system comprising the first part 110 and the second part 120. This damping coefficient effectively dampens the oscillatory behavior of the first part relative to the second part. For example, a collar of closed cell foam may be disposed around the flexible air flow duct 170 shown in FIG. 1, or a collar of closed cell foam may even constitute the flexible air flow duct 170.

Preferably, the first portion 110 is vibrationally isolated from the second portion 120 by one or more resilient elements 210 in addition to the at least one damping member 170, 1910, since metal springs are more effective in vibrationally isolating components from one another, wherein the one or more resilient elements 210 comprise at least one metal spring. Thus, the combination of the metal spring and the resilient material damping member together provide effective vibration isolation and reduced risk of producing an elliptical cutting disk during operation of the severing tool.

FIG. 19 illustrates two example types of damping members that may be used independently or in combination with each other. It should also be understood that the present teachings encompass other types of damping members applied at other locations between the first and second portions. For example, between … may also be construed to encompass a damping member that is attached to both the first and second portions, but extends outside of the slot 1930 formed between the first and second portions.

FIG. 20 illustrates two example damping members 1910, 1920. The first damping member 170 is integral with a bellows 2100 (shown in more detail in fig. 21) or other flexible airflow conduit disposed between the first portion 110 and the second portion 120. This bellows or flexible airflow conduit provides a damping coefficient as described above to provide a desired damping ratio and also serves to limit the stroke length associated with the relative movement of the first portion 110 with respect to the second portion 120. When the first part 110 is moved in the direction C shown in fig. 21 towards the second part 120, the stiffening elements 1920 arranged on at least one side of the bellows, e.g. on two or more sides of the bellows 2100, limit the compression of the bellows, thereby limiting the stroke length of the oscillating movement, thus disturbing the oscillating behavior.

The compressibility of the bellows, which is associated with the shore hardness, may be adjusted by selecting the type of material used for the stiffening element 1920 or by sizing the thickness of the material used in the element and the bellows in order to obtain a desired damping ratio of the damped mass spring system comprising the first and second portions. As shown in fig. 21, compressibility can also be adjusted by disposing one or more cavities 1930 in the stiffening element 1920. According to aspects, the bellows 2100 is arranged between the first portion 110 and the second portion 120, wherein the bellows 2100 is associated with a shore durometer value or shore hardness measured with a type a durometer according to DIN ISO 7619-1 of between 50-100, preferably between 65-90. It will therefore be appreciated that the shore hardness and material thickness of a bellows such as that shown in fig. 4 and/or 21 may be adjusted to mitigate the presence of an oval cutting disk in a hand-held power severance tool by: or introducing a damping coefficient in the mass-spring system to dampen oscillations; or introduce a limit on the stroke length to disturb the oscillation; or both.

According to another example, as also shown in fig. 20, at least one damping member 1910 is fixedly attached to one of first portion 110 or second portion 120 and is disposed at a distance from the other of first portion 110 or second portion 120. Accordingly, the at least one damping member 1910 is arranged to limit the stroke length associated with relative movement of the first portion 110 with respect to the second portion 120. This damping member has a function similar to that of the stiffening element 1920 discussed above in connection with fig. 21. Which is positioned to limit the stroke length of the oscillating movement between the first and second portions and thus to disturb any oscillating behavior of the first portion 110 relative to the second portion 120. A more detailed view of damping member 1910 is shown in figure 22. According to this example, it is integrally formed from a single piece of resilient material and mounted on the body of the first portion 110 or the second portion 120.

Alternatively, damping member 1910 or some other resilient element may be attached to both first portion 110 and second portion 120, thereby forming a resilient bridge between these components. Since the damping member is associated with a damping coefficient, the damping ratio of the resulting damped mass spring system will be affected by the addition of such a damping member and the tendency of the elliptical cutting disks may be mitigated.

An electrical recoil protection mechanism can advantageously be implemented since the cutting disc speed can now be kept low without the risk of creating an oval cutting disc. This is because the kick-back protection mechanism based on the braking of the motor 140 may not be effective at very high cutting disc speeds. Thus, according to some aspects, the motor 140 is arranged to be controlled by the control unit of the severing tool via a motor control interface. The control unit is arranged to obtain data indicative of the angular velocity of the cutting disc 130 and to detect a kickback condition based on the reduction in angular velocity. The control unit is further arranged to control the electromagnetic braking of the motor 140 in response to detecting a kickback condition.

To provide a kick-back mitigation function also suitable for high power cutoff tools associated with significant tool inertia that are fast enough in response and have sufficient braking force, a hand-held power cutoff tool for cutting concrete and stone with a rotatable cutting disk 130 is disclosed herein. The severing tool comprises a motor 140 arranged to be controlled by a control unit via a motor control interface. The control unit is arranged to obtain data indicative of the angular velocity of the cutting disc 130 and to detect a kickback condition based on the reduction in angular velocity. The control unit is further arranged to control electromagnetic braking of the motor 140 in response to detecting a kickback condition, and optionally is further arranged to actively regulate energy output from the motor via the control interface during electromagnetic braking.

The detection mechanism is based on monitoring the angular velocity of the cutting disc 130. If a sudden decrease in speed is seen, such as a high level of delay in the electrical rotor angle or cutting disc angle, a kickback condition is detected. The motor is forcibly braked immediately after the control unit detects the kickback event, so as to mitigate the influence of the kickback event. Such braking involves actively controlling the energy output from the motor in order to provide positive power without damaging the electrical components of the severing tool. This braking is facilitated by the fact that the cutting disc is operated at a speed below 3500rpm, for example at 3200rpm, which is made possible by the presence of the damping member.

The backlash detection and braking of the cutting disc is usually so fast that the blade stops even before it leaves the object being processed. Even if some kickback motion occurs, the energy transferred from the cutting disc 130 to the machine body will be reduced to a level that mitigates the detrimental effects of the kickback event. It is worth noting that the motor is not merely disconnected from the power supply as in many prior art documents. Instead, the energy output from the motor is actively regulated to provide a strong enough braking action to stop the kickback event.

Referring also to fig. 1, fig. 23 shows details of a handheld power cut-off tool 2300 including a fan 145 arranged to be driven by a motor 140 to generate a cooling airflow 160, and a battery compartment 150 including an electrical storage device 220, 1800, such as a battery, arranged to power the motor 140. The cooling air duct is arranged to direct the cooling air flow 160 towards an outlet aperture 1750 (seen, for example, in fig. 17B) formed in the wall of the battery compartment 150. The outlet holes 1750 face corresponding inlet holes 1870 formed in the housing of the electrical storage device 220, 1800 for receiving cooling air to generate a pressure of air above atmospheric pressure in the electrical storage device 220, 1800. Referring to fig. 24, which more schematically illustrates the cooling airflow, the first slot segment Ss1 is formed by the distance between the outlet aperture 1750 and the inlet aperture 1870 on the electrical storage device 220 such that the first portion 2415 of the cooling airflow 160 leaks out of the shut-off tool through the first slot segment Ss 1.

This first portion 2415 of the cooling airflow 160 creates an air pressure within the first slot segment that must be overcome by the dust and mud entering the slot between the electrical storage device 220 and the compartment walls. Thus, dust and mud is prevented from entering the slot and the battery compartment is kept clean, which is an advantage. The clean battery compartment, free of accumulated dust and mud, simplifies insertion and removal of the electrical storage device 220 from the tool.

A first portion 2415 of the cooling airflow is directed transverse to the total cooling airflow 160 into the electrical storage device 220, 1800. Furthermore, the first part may leak on both sides of the shut-off tool, i.e. from both sides of the battery compartment through hole.

According to one example, first slot segment Ss1 is bounded on one side by a guide device that guides electrical storage device 220 into the compartment. First slot segment Ss1 may also be defined by support heel 1710. It should be noted, however, that slot segments Ss1, Ss2, and Ss3 may be connected to one another or defined by other defining means.

According to aspects, the distance between the electrical storage device 220, 1800 and the wall of the battery compartment 150 is between 0.5mm and 2.0mm, preferably about 1.0 mm. This distance may vary around the electrical storage device 220.

The electrical storage device 220, 1800 may also include one or more electrical connectors 1840 arranged to mate with corresponding contact strips 1740 arranged in the battery compartment 150. One example of these electrical connectors is more clearly seen in fig. 18C. An opening is formed in the housing of the electrical storage device 220, 1800 that connects with the electrical connector 1840 so that the second portion 2425 of the cooling air flow passes through the opening and leaks out of the shut-off tool via the second slot segment Ss2 formed between the electrical storage device 220, 1800 and the wall of the battery compartment 150. Thus, since the battery housing is not hermetically sealed around the electrical connector 1840, the overpressure of the cooling air inside the electrical storage device 220 creates an airflow that exits via the electrical connector and passes via the second slot segment. Also, if it is to enter the slot, this airflow leaving the machine via the slot must be overcome by the dust and mud. This is not possible because the leakage is a considerable flow with respect to the more diffuse movement of dust and mud generated by the cutting operation. Thus, the electrical connector remains clean and free of mud during operation, which is an advantage, in particular because it becomes easier to insert and remove the electrical storage device 220 if the connector and the guiding device are clean. The second slot segments Ss2 may be defined, for example, by upper ridges 1820 and lower ridges 1830 as shown in fig. 18C.

Finally, an air outlet 1860 may also be formed in the electrical storage device housing opposite the inlet aperture 1870 to form a channel for cooling air to flow through the electrical storage device. The third slot segment Ss3 may be formed by the distance between the air outlet 1860 and the wall of the battery compartment 150, such that the third portion 2435 of the cooling airflow 160 leaks outside of the shut-off tool via the third slot segment Ss 3. This third slot segment also provides a passage for cooling air to leak through the slot, keeping the space between the top of the power device 220 and the cell compartment walls clean and free of dust and mud.

Fig. 25 schematically illustrates a mass distribution of a work tool, such as the severing tool discussed above in connection with fig. 1-24. It has been found that the weight distribution between the components of a hand-held power cut-off tool comprising a first part and a second part arranged in vibration isolation from each other can be optimized in order to obtain a more efficient cutting operation while reducing operator discomfort due to the propagation of vibrations from the machine to the operator via the handle.

A debouncing gasoline fuel cutoff tool is known, i.e., an internal combustion engine power tool. However, these known tools have a suboptimal weight distribution between the handle components and the components that comprise the internal combustion engine and the cutting disc. Some known gasoline power cut-off machines have a handle portion that weighs about 2600g when empty of the fuel tank and 3500g when full of the fuel tank, as compared to the electric motor, and have an arm portion that weighs about 7550g, i.e., an empty tank ratio of 2600g/10150g (which is equal to about 0.25), and 3500g/11050g (which is about 0.32) when full of the tank. The ratio of full case can be compared to the case where the battery (mass M3) fits in the mass M2 (i.e., M2+ M3), while the case of empty case can be compared to the case where there is no battery (i.e., only M2).

It is advantageous if the part with the handle, i.e. the masses M2 and M3 in fig. 25, has sufficient weight to withstand the vibrations propagating through the damping and resilient elements described above. However, the parts with cutting blades, i.e. masses M1 and M4, cannot be too light relative to the handle part, as this would result in an unbalanced tool.

It has been found through a lot of experiments and computer analysis that the ratio of the second mass M2 to the sum of the first and second masses M1+ M2 should preferably be at least 0.3, preferably more than 0.35, i.e. the second mass should constitute a substantial part of the total mass of the severing tool without the cutting disc and the electrical storage device mounted. For example, the ratio M2/(M1+ M2) may be about 0.38 for a 12 inch blade set and about 0.37 for a 14 inch blade set. However, the second mass M2 should not be too large relative to the first mass. Therefore, the ratio of the second mass M2 to the sum of the first and second masses M1+ M2 should preferably be below about 0.5, preferably below about 0.6.

It has also been found that the ratio of the sum of the second and third masses (i.e. M2+ M3) to the sum of the first and fourth masses (M1+ M4) should be at least 0.6, preferably greater than 0.8, even more preferably greater than 1.0. These ratios provide a well-balanced tool with excellent vibration resistance.

It has also been found that the ratio of the sum of the second and third masses (M2+ M3) to the sum of the weight of the entire arrangement including the electrical energy storage device and the cutting discs (i.e. M1+ M2+ M3+ M4) should be at least 0.45, preferably greater than 0.5. This ratio provides a stable tool with good vibration resistance characteristics.

In summary, disclosed herein is a hand-held power severance tool 100, 200, 800, 1000, 1900, 2500 comprising a first portion 110 and a second portion 120 arranged in vibration isolation from one another.

The first portion 110 comprises an interface 2510 for holding the cutting tool 130 and a motor 140 arranged to drive the cutting tool, wherein the first portion is associated with a first mass M1.

The second part 120 comprises a battery compartment 150 for holding an electrical storage device 220 arranged to supply power to the motor 140, and a front handle 190 and a rear handle 195 for operating the shut-off tool, wherein the second part is associated with a second mass M2.

Wherein the ratio of the second mass M2 to the sum of the first and second masses M1+ M2 is at least 0.3, preferably greater than 0.35.

Also disclosed herein is a hand-held powered severance tool 100, 200, 800, 1000, 1900, 2500 comprising a first portion 110 and a second portion 120 arranged in vibrational isolation from one another, a cutting tool 130, and an electrical storage device 220.

The first part 110 comprises an interface 2510 for holding a cutting tool 130 and a motor 140 arranged to drive the cutting tool, wherein the first part is associated with a first mass M1, and wherein the cutting tool is associated with a fourth mass M4.

The second part 120 comprises a battery compartment 150 for holding an electrical storage device 220 arranged to supply power to the motor 140, and a front handle 190 and a rear handle 195 for operating the shut-off tool, wherein the second part is associated with a second mass M2, and wherein the electrical storage device 220 is associated with a third mass M3.

Wherein the ratio of the sum of the second and third masses M2+ M3 to the sum of the first and fourth masses M1+ M4 is at least 0.6, preferably greater than 0.8, even more preferably greater than 1.0.

Further, disclosed herein is a hand-held power severance tool 100, 200, 800, 1000, 1900, 2500 comprising a first portion 110 and a second portion 120 arranged in vibration isolation from each other, a cutting tool 130, and an electrical storage device 220.

The first part 110 comprises an interface 2510 for holding a cutting tool 130 and a motor 140 arranged to drive the cutting tool, wherein the first part is associated with a first mass M1, and wherein the cutting tool is associated with a fourth mass M4.

The second part 120 comprises a battery compartment 150 for holding an electrical storage device 220 arranged to supply power to the motor 140, and a front handle 190 and a rear handle 195 for operating the shut-off tool, wherein the second part is associated with a second mass M2, and wherein the electrical storage device 220 is associated with a third mass M3.

Wherein the ratio of the sum of the second and third masses (M2+ M3) to the sum of the weights of the entire arrangement comprising the electrical energy storage device and the cutting discs (M1+ M2+ M3+ M4) is at least 0.45, preferably greater than 0.5.

The following table provides example weight distributions that may be advantageously used with the hand-held power severance tools discussed herein. Examples of two different sized cells have been included in the table, with the large cell weighing about 5100g (denoted as M32) and the smaller cell weighing about 3000g (denoted as M31).

Example weight of parts	12 inch blade	14 inch blade
			M1	4500g	4720g
M2	2750g	2750g
			M31-small cell	3000g	3000g
M32-big battery	5100g	5100g
			M4	1250g	1850g
			Relationships between
M2/(M2+M1)	～0.38	～0.37
			(M2+M31)/(M1+M4)	～1.0	～0.88
(M2+M32)/(M1+M4)	～1.37	～1.19
(M2+M31)/(M1+M2+M31+M4)	0.5	～0.47
			(M2+M32)/(M1+M2+M32+M4)	～0.58	～0.54