EP2269772B1 - Ratchet wrench with reinforced torque - Google Patents

Description

Technical area

The invention is in the field of manually operable tools and relates to a ratchet wrench or ratchet wrench with a torque gain according to the preamble of the first claim.

Such a ratchet wrench is for example from the US 2006/0090606 known.

State of the art

In the DE-2643552 A1 a ratchet wrench for high torque with two parallel side plates and a ratchet wheel and an associated pawl is described. The tool is actuated by tangentially introduced tensile and compressive forces, which act directly on a rotatably mounted in parallel side plates latch. The tool has neither a torque ratio nor a reverse rotation. Although the pawl has several teeth to divide the high tangential forces. Due to the elastic deformation of the teeth and the entire pawl, however, the load is distributed very differently to the individual teeth. With more than three teeth, these deformations can even lead to individual teeth no longer wear.

• Die Linearführung der Klinke neigt zum Verkanten bzw. Verklemmen
• Mehr als zwei Zähne pro Klinke haben eine zu unterschiedliche Lastverteilung zur Folge.
• Hohe Biegebeanspruchung des Antriebshebels infolge des Langlochs
• Die Gleitstiftverbindung mit metallischem Kontakt führt zu grosser Reibung und hohem Verschleiss.
• Aufwändige und teure Herstellung der beiden Halbschalen.
• Keine Rückdrehsicherung vorhanden.
• Die Antriebsdrehrichtung ist entgegengesetzt zur Abtriebs-Drehrichtung. Dies ist sehr unangenehm, weil man intuitiv den Antrieb in dieselbe Drehrichtung betätigen möchte wie das anzuziehende oder zu lösende Befestigungsmittel.

The US-5953966 A discloses a ratchet wrench with a torque ratio. The tool has two half-shells with integrated side walls and with one opening for the drive (square socket wrench) and the output (hexagon) for turning nuts or bolts. The torque transmission takes place via a short pivot lever on the drive side, which acts by means of a sliding pin on a longer output side pivot lever. The sliding pin has two key surfaces and is guided in a slot of the drive lever. The output side pivot lever is equipped with a multi-toothed pawl and is also guided in an arcuate, concentric to the output extending web. This ratchet wrench has the following disadvantages:

• The linear guide of the pawl tends to jamming or jamming
• More than two teeth per pawl result in too different load distribution.
• High bending stress of the drive lever due to the slot
• The Gleitstiftverbindung with metallic contact leads to great friction and high wear.
• Elaborate and expensive production of the two half-shells.
• No reversing safety device available.
• The drive direction of rotation is opposite to the output direction of rotation. This is very uncomfortable because you want to intuitively operate the drive in the same direction as the tightening or to be solved fastener.

• Sehr aufwändige und teure Lösung mit Zahnradpaar und Nockenwelle.
• Hohe Bauweise infolge der Zahnrad- und Exzenternocken-Übersetzung.
• Hohe Flächenpressungen beim Nocken-Rollenkontakt.
• Aufwändige und teure Herstellung der beiden Halbschalen.

In the US-3564953 A a flat ratchet wrench with a torque ratio is described. The tool has analogous to that of the US-5953966 A Two half shells with integrated side walls and one opening for the drive (square socket wrench) and the output (square) for turning nuts or bolts on. The drive takes place in this ratchet wrench in a continuous rotational movement, and the torque gain takes place by means of gear ratio and an eccentric cam, which acts on a Abtriebshebelarm. The output lever arm encloses at its other end a ratchet wheel which has a corresponding tool receiving opening in its center. The oscillating pivoting movement of this output lever arm is converted by means of a ratchet, which rotates with the lever, and a pawl, which is supported on the housing, in a stepwise and rectified rotational movement of the ratchet wheel. This ratchet screwdriver has the following disadvantages:

• Very complex and expensive solution with gear pair and camshaft.
• High construction due to the gear and eccentric cam translation.
• High surface pressures at the cam roller contact.
• Elaborate and expensive production of the two half-shells.

• Asymmetrische Belastungen durch "fliegende" Lagerungen.
• Keine Rückdrehsicherung vorhanden.
• Freiläufe sind für eine hohe und drehsteife Drehmomentübertragung ungeeignet.

The EP-0027183B1 describes a wrench in which a driven lever with integrated pivot and key nut is rotatably mounted in a support foot. Also in the support foot laterally offset a drive lever is mounted, which causes a lever linkage from the drive lever to the output lever with a connecting link. As an additional option, an in Output lever integrated freewheel, which acts on a coaxially arranged Schlüsselelnusshülse and allow the free turning back of the output lever specified. This wrench has the following disadvantages:

• Asymmetric loads due to "flying" bearings.
• No reversing safety device available.
• Freewheels are unsuitable for high and torsionally stiff torque transmission.

Brief description of the invention

It is an object of the present invention to avoid at least some of the disadvantages found in the prior art. In particular, the ratchet wrench according to the invention should be suitable for very high torques without overloading and deformations occurring. Its construction should be simple and its manufacture inexpensive. The operating direction of the drive lever and the direction of rotation of the output gear should be identical, the ratchet wrench should have a reverse rotation.

These and other objects are achieved by the ratchet wrench or ratchet wrench defined in claim 1. Advantageous embodiments are given in the dependent claims.

Accordingly, the inventive torque wrench ratchet wrench includes a housing, externally accessible torque receiving means on the housing for receiving drive torque, externally accessible torque output means on the housing for output torque greater than the drive torque, and connection means housed in the housing for establishing operative engagement therebetween Torque receiving means and the torque output means and for amplifying the drive torque in the output torque. The connecting means include an output lever, an output gear operatively connected to the torque output means, and a ratchet mechanism acting between the output lever and the output gear.

The torque receiving means, the torque output means and the connecting means are substantially surface symmetric with respect to a common plane of symmetry. The housing is closed by two parallel to the plane of symmetry, preferably also symmetrical with respect to the plane of symmetry housing plates which are spaced apart by at least one housing spacer and connected to this form-fitting. The output lever includes two parallel to the plane of symmetry also preferably symmetrical with respect to the plane of symmetry lever plates, which are spaced apart from each other by at least one lever spacer and positively connected thereto. The housing plates, the at least one housing spacer, the lever plates and the at least one lever spacer are substantially flat plates, the form-fitting. preferably by means of cylindrical pins, are interconnected and preferably made of metal.

According to a further aspect of the invention, the ratchet mechanism includes at least two ratchet elements, each of which is independently pivotable about its own ratchet axis and adapted to engage in a corresponding toothing of the driven gear.

In a further preferred embodiment, the ratchet wrench includes a reverse rotation locking mechanism acting between the housing and the driven wheel. The anti-rotation mechanism ensures that the movement of the output gear is rectified, d. H. always in one direction, albeit gradually. The anti-rotation locking mechanism preferably includes at least two pawl members, each of which is independently pivotable about its own pawl axis and adapted to engage in a corresponding toothing of the driven gear. The ratchet and pawl elements can be made of flat plates and are preferably identical. They can be made by water jet cutting, precision casting, precision forging or sintering, e.g. B. high-strength tempered steel or tool steel.

At least two ratchet elements and / or at least two pawl elements can for mutual transmission of forces and / or torques through be set up direct mutual mechanical contact. At least one of the ratchet elements and / or at least one of the pawl elements can be pressed by a spring element against the driven gear. Preferably, a group consisting of at least two ratchet elements and / or at least two pawl elements is pressed against the output gear by a common spring element. The common spring element presses on a first of the ratchet elements, and each of the other ratchet elements of the group is actuated, as it were by a domino effect, from the respective preceding one. It is advantageous to use a leaf spring for this purpose. Of course, other spring elements such as spiral compression springs or elastomeric fittings could be used. The leaf spring is preferably made in one piece and two layers.

A housing spacer can serve as a bearing for the at least two pawl elements. A lever spacer can serve as a bearing for the at least two ratchet elements. The spacers are preferably in one piece, but may also be constructed of two or more thinner, stacked plates.

In a further preferred embodiment, the torque receiving means and / or the torque output means each have a form element for receiving a shaft. The connecting means are designed such that the driving torque and the output torque are rectified, i. H. By means of pivotal movements during the drive a rectified output rotary motion is generated. The operator would like to intuitively pull the drive in the same direction in which the fastener is to be rotated.

Due to the perfect symmetry of the ratchet wrench is evenly loaded. so that unwanted bending or torsional loads omitted. In addition, the ratchet wrench can be easily turned to reverse the direction of rotation. The ratchet wrench is characterized by a particularly simple structure and a cost-effective production. The plate-shaped elements can be produced easily and very accurately, for example by laser or water jet cutting. All power transmission between the ratchets and the lever spacer or between the pawls and the housing takes place positively via the cylindrical pins. Additionally or alternatively, the plates and the spacers could preferably be connected to one another in a material-locking manner, for example by soldering, only on one side.

Brief description of the drawings:

Figur 1

eine Ansicht auf eine erste Ausführungsform des erfindungsgemässen Ratschenschlüssels,

Figur 2

eine Seitenansicht des Ratschenschlüssels gemäss Figur 1 ohne Abdeckband,

Figur 3

eine Draufsicht des Ratschenschlüssels gemäss Figur 1 mit Abdeckband,

Figur 4

eine Ansicht auf den Ratschenschlüssel gemäss Figur 1 ohne vordere Gehäuse-platte,

Figur 5

eine Ansicht auf den Ratschenschlüssel gemäss Figur 4 ohne vorderes Ratschenblech,

Figur 6

einen Schnitt entlang dem Linienzug A-A in Figur 5,

Figur 7

eine Ansicht auf den Ratschenschlüssel gemäss Figur 5 in der Endposition des Antriebs,

Figur 8

einen Schnitt entlang dem Linienzug B-B in Figur 7,

Figur 9

eine Ansicht auf eine zweite Ausführungsform des erfindungsgemässen Ratschenschlüssels ohne vordere Gehäuseplatte,

Figur 10

einen Ausschnitt im Bereich der Klinken einer dritten Ausführungsform des erfindungsgemässen Ratschenschlüssels,

Figur 11

eine Ausschnitt im Bereich der Klinken einer vierten Ausführungsform des erfindungsgemässen Ratschenschlüssels,

Figur 12

eine Ausschnitt im Bereich der Klinken einer fünften Ausführungsform des erfindungsgemässen Ratschenschlüssels,

Figur 13

eine Ausschnitt im Bereich der Klinken einer sechsten Ausführungsform des erfindungsgemässen Ratschenschlüssels,

Figur 14

eine Ausschnitt im Bereich der Klinken einer siebten Ausführungsform des erfindungsgemässen Ratschenschlüssels,

Figur 15

einen Schnitt entlang dem Linienzug C-C in Figur 14,

Figur 16

einen Schnitt entlang dem Linienzug C-C in Figur 14 in einer zweiten Ausführungsvariante im Bereich der Klinke bzw. Ratschenlagerung,

Figur 17

eine Ansicht auf die erste Ausführungsform des erfindungsgemässen Ratschenschlüssel entsprechend Figur 1 beim Einsatz in einer Flanschverschraubung,

Figur 18

eine Draufsicht auf den Ratschenschlüssel gemäss Figur 17 beim Einsatz in einer Flanschverschraubung und

Figur 19

eine Ansicht auf die zweite Ausführungsform des erfindungsgemässen Ratschenschlüssels entsprechend Figur 9 beim Einsatz in einer Flanschverschraubung.

The invention will be explained in detail with reference to drawings. Hereby show:

FIG. 1

a view of a first embodiment of the inventive ratchet wrench,

FIG. 2

a side view of the ratchet wrench according FIG. 1 without masking tape,

FIG. 3

a plan view of the ratchet wrench according FIG. 1 with masking tape,

FIG. 4

a view of the ratchet wrench according FIG. 1 without front housing plate,

FIG. 5

a view of the ratchet wrench according FIG. 4 without front ratchet plate,

FIG. 6

a section along the line AA in FIG. 5 .

FIG. 7

a view of the ratchet wrench according FIG. 5 in the final position of the drive,

FIG. 8

a section along the line BB in FIG. 7 .

FIG. 9

a view of a second embodiment of the inventive ratchet wrench without front housing plate,

FIG. 10

a detail in the region of the pawls of a third embodiment of the ratchet wrench according to the invention,

FIG. 11

a detail in the region of the pawls of a fourth embodiment of the inventive ratchet wrench,

FIG. 12

a detail in the region of the pawls of a fifth embodiment of the ratchet wrench according to the invention,

FIG. 13

a detail in the region of the pawls of a sixth embodiment of the ratchet wrench according to the invention,

FIG. 14

a detail in the region of the pawls of a seventh embodiment of the inventive ratchet wrench,

FIG. 15

a section along the line CC in FIG. 14 .

FIG. 16

a section along the line CC in FIG. 14 in a second embodiment in the region of the pawl or ratchet bearing,

FIG. 17

a view of the first embodiment of the inventive ratchet wrench accordingly FIG. 1 when used in a flange connection,

FIG. 18

a plan view of the ratchet wrench according to FIG. 17 when used in a flange connection and

FIG. 19

a view of the second embodiment of the inventive ratchet wrench accordingly FIG. 9 when used in a flange screw connection.

Ways to carry out the invention

The FIG. 1 shows a view of the ratchet wrench with torque gain, the FIGS. 2 and 3 the corresponding side and top views. Two identical housing plates 7 close a ratchet wrench housing up and down. They have bearing bores 8 and 9, in which a driven wheel or ratchet wheel 1 with two bearing pins 3 (see FIG. 6 ) and a drive lever 30 is mounted with two bearing journals 31. The two housing plates 7 are by means of screws 51, which in corresponding threaded holes 16 of a spacer plate 12 and in a spacer 17 (see FIG. 4 ), fastened. The screws 51 are preferably countersunk screws, which are embedded in corresponding countersinks 11. As additional security will the driven gear 1 axially fixed by means of two retaining rings 6. A cover tape 50, which is preferably made of spring steel strip covers the lateral openings between the two housing plates 7 completely, so that the mechanism is protected from contamination and damage by foreign particles.

The FIG. 4 shows the ratchet wrench according to FIG. 1 without front housing plate 7. In this illustration, the torque transmission is illustrated. The drive lever 30 has a shaped element 32, preferably a standardized inner square, in which a commercial tool can be applied. The drive lever 30 acts on its small drive lever length 56 by means of a connecting rod 36 on two symmetrically arranged, acting as output lever ratchet plates 20 (see also FIG. 6 ) with a large output lever length 57. The lever ratio. that is, the ratio of the drive lever length 56 to the output lever length 57, should be less than one in any case, so that a corresponding torque transmission takes place. It is z. B. between 1: 1.5 and 1:20, preferably between 1: 2 and 1:10 and in the present embodiment is about 1: 5.

In the FIG. 5 In addition, the upper ratchet plate 20 is removed. In this presentation and by the FIGS. 6 and 8 the positioning of the two housing plates 7 and the two ratchet plates 20 is illustrated by means of cylindrical pins 48 and 49, respectively.

The cylinder pins 48, 49 are preferably made of hardened steel and frictionally in holes 15 and 28 of the spacers 12, 17 and 25 connected. The cylindrical pins 48, 49 protrude from both sides of the spacers 12, 17 and 25 and engage in corresponding holes 10, 23 of the housing plates 7 and the ratchet plates 20 a.

As FIG. 8 illustrates, the drive lever 30 is symmetrical and has, in addition to the two bearing pin 31, two side cheeks 35, in which a first connecting rod pin 38 is pressed force fit. In the same way a second, preferably identical connecting rod bearing pin 38 is fastened non-positively in a bore 22 of the ratchet plates 20. To minimize friction the two connecting rods 38 in special plain bearing bushes 37, which are recessed frictionally in the connecting rod 36. The connecting rod bearing bushes 37 are preferably commercially available bearing bushes, which are produced, for example, from wear-resistant plastic (eg PTFE, PI) and / or from sintered metal.

The FIG. 5 shows the ratchet mechanism in the initial position of the drive lever 30. In this case, a stop surface 34, which is formed by side cheeks 35 of the drive lever 30, with a stop 18 of the spacer plate 12 in contact. The FIG. 5 also shows two pawls 40 with their teeth 41 in engagement with a toothing 4 of the driven wheel 1, while two ratchets 44 are still outside the teeth 4 of the driven wheel 1.

Both the two pawls 40 and the two ratchets 44 are each pressed by a leaf spring 43 and 47 against the driven wheel 1. The leaf springs 43 and 47 are positively anchored in club-shaped slots 14 and 27 of the spacers 12 and 25 and are made of one or more sheet metal layers.

The actuation force on the not acted upon by the leaf spring 43 and 47 pawl 40 or ratchet 44 is effected by direct, immediate contact between the pawls 40 and ratchets 44th By this package formation of the pawls 40 and ratchets 44 without additional intermediate elements and the actuation with only one spring element 43 or 47 can realize a particularly space-saving and reliable solution.

Due to the extremely high forces, it is necessary to distribute the reaction force of the toothing 4 of the driven wheel 1 on a plurality of teeth 41 and 45 of the driven wheel 1. It is particularly advantageous to use a plurality of pawls 40 or ratchets 44, because then the load is evenly distributed to the teeth 4, more precisely to the teeth 41 and 45, respectively. A single pawl 40 or ratchet 44 should cover an angle of at most 25 ° of the teeth 4 of the driven wheel 1; the angle is z. B. between 3 ° and 25 ° and preferably between 10 ° and 20 °. As a result, on the one hand the pivoting operation is facilitated in the toothing 4 and on the other hand slipping of the pawls 40 and ratchets 44 prevents.

The two pawls 40 are rotatably mounted with their bearing pins 42 in holes 13 of the spacer plate 12, the two ratchets 44 with their bearing pins 46 rotatably mounted in bores 26 of the spacer 25. The bearing bores 13 and 26 are designed as cylindrical recesses with a lateral opening, wherein the overlap angle with the pawl or ratchet bearing pin 42, 46 is more than 190 °. This has the advantage that the pawls 40 or ratchets 44 are connected in a simple manner in a form-fitting but rotatable manner with the associated spacers 12 and 25, respectively.

A section along the line AA of FIG. 5 is in the FIG. 6 shown. According to the invention, the ratchet wrench is substantially surface-symmetrical with respect to a common plane of symmetry S, which lies parallel to the housing plates 7 and the ratchet plates 20.

In the FIG. 7 the drive lever 30 is shown in its end position. This position is defined by a stop surface 19 of the spacer 17 and a support nose 39 on the connecting rod 36. In contrast to FIG. 5 Here are the two ratchets 44 with their teeth 45 in engagement with the teeth 4 of the driven wheel 1, while the two pawls 40 are still outside the teeth 4.

By the alternating pivoting movement 58 (see FIG. 4 ) of the drive lever 30 and the alternate engagement of the pawls 40 and ratchets 44 in the toothing 4, a rectified and stepwise rotary motion 59 of the driven wheel 1 is generated.

The FIG. 8 shows a section along the line BB of FIG. 7 , Again, the surface symmetry of the inventive ratchet wrench with respect to the plane of symmetry S is clearly visible.

The FIG. 9 shows a view of a second embodiment of the inventive ratchet wrench without front housing plate. According to this second embodiment, an extension arm 55 is positively or materially connected to the drive lever 30; otherwise it is analogous to the first embodiment of FIG. 1 , The second embodiment then has advantages if the space conditions do not allow the attachment of a commercial Stechschlüssels the inner square 32.

The FIGS. 10 to 13 show further embodiments of pawls 40, 140 and their operation by means of a spring element 143. The ratchet 44 (see FIGS. 5, 7 ) can be configured in an analogous manner. The spring element 143 may be made of a metal, but alternatively also of another material, for example of a plastic or an elastomer solid or hollow profile (not shown).

In the FIG. 10 is used instead of a leaf spring 43 (see FIGS. 5, 7 ) uses a conical coil spring 143, which is embedded in a recess 114 of the spacer 12.

The FIG. 11 shows a pair of pawls 40, 140, in which a first pawl 40 two teeth 41 and a second pawl 140 three teeth 141 have.

The embodiment of FIG. 12 has three identical pawls 40, which are actuated by means of a two-layered leaf spring 143. With this embodiment, much higher forces can be transmitted. It is particularly advantageous if the two-layered leaf spring 143 is made in one piece as shown. As a result, the positive anchoring in a club-shaped recess 144 can be made particularly advantageous. Of course, the leaf spring 143 could also be made of three or more sheet metal layers (one or more parts) to achieve the desired spring properties.

The FIG. 13 shows an embodiment with five ratchets 144, which each have only one ratchet tooth 145. This embodiment requires relatively long ratchets 144 or pawls, so that the desired positive anchoring can be realized in the bearing bores 126.

A much more compact design variant for one-tooth pawl and / or ratchet packs is in the Figures 14-16 illustrated by the example of the ratchet package 244. The support of the ratchets 244 via the cylindrical ends 246 on the likewise cylindrical bearing bores 226. Since in this compact design no positive connection such as analogous to FIG. 7 can realize the retention of the ratchets 244 is realized by means of a double-sided on each ratchet 244 projecting pin 53 which is anchored in corresponding holes 52 'of the ratchet plates 20. In the embodiment according to the FIG. 15 is a long, continuous pin 53 in a bore 52 frictionally connected, preferably by means of a press-fit connection with the ratchet 244. In the variant according to FIG. 16 two short pins 153 are used, one half of which are pressed into the holes 52 'of the ratchet plates 20 and the other halves slidingly project into the retaining hole 52 of the ratchet 244 and thus allow rotation of the ratchet 244 with simultaneous positive engagement.

The FIGS. 17 and 18 show the inventive ratchet wrench in a first embodiment according to the FIG. 1 when tightening a screw 61, 161, 162, 62, 162, 262 in a flange 163, 164 and 63, 64 with a plurality of fasteners. For actuating the drive lever 30, a commercially available torque wrench 60 is used with which the required drive torque is applied.

The ratchet wrench is supported with its support region 54 on the adjacent nut 162 (to the right of the nut 62 to be tightened), by means of which the reaction force occurring is absorbed. In the area of the support 54, an additional (not shown) extension arm can be attached, by means of which the ratchet wrench can be supported on a farther fixed base.

When changing the direction of rotation (not shown), for example for loosening the screw 62, the ratchet wrench is rotated by 180 degrees placed on the fastener 62 so that its housing plate 7, which was on top when tightening, now lies down. The operation of the drive lever 30 with the torque wrench 60, which now also on the opposite side in the inner square 32 (see FIG. 1 ) is used, now causes the stopper 54 is supported at the adjacent nut 262 (left of the mother to be solved 62).

The FIG. 19 shows the ratchet wrench with the integrated extension arm 55 according FIG. 9 already on the occasion of the FIGS. 17, 18 described screwing.

Claims (15)

1. A ratchet wrench having torque boost, containing a housing (7, 12, 50), externally accessible torque receiving means (32) on the housing (7, 12, 50) for receiving a drive torque, externally accessible torque delivery means (2) on the housing (7, 12, 50) for delivering an output torque, which is greater than the drive torque, and connecting means (30, 36, 20, 44, 4, 1), which are housed in the housing (7, 12, 50), for establishing an operational connection between the torque receiving means (32) and the torque delivery means (2) and for boosting the drive torque into the output torque, these connecting means (30, 36, 20, 44, 4, 1) containing an output lever (20, 25), an output wheel (1), which is operationally connected to the torque delivery means (2), and a ratchet mechanism (44, 4) acting between the output lever (20, 25) and the output wheel (1), wherein the torque receiving means (32), the torque delivery means (2), and the connecting means (30, 36, 20, 44, 4, 1) are essentially surface-symmetrical with respect to a shared plane of symmetry (S), characterized in that the housing (7, 12, 50) is terminated by two symmetrical housing plates (7), which are parallel to the plane of symmetry (S), and are preferably also symmetrical with respect to the plane of symmetry (S), and which are spaced apart from one another by means of at least one housing spacer part (12, 17) and are connected thereto in a formfitting manner, the output lever (20, 25) contains two lever plates (20), which are parallel to the plane of symmetry (S) and are preferably also symmetrical with respect to the plane of symmetry (S), and which are spaced apart from one another by at least one lever spacer part (25) and are connected thereto in a formfitting manner, and the housing plates (7), the at least one housing spacer part (12, 17), the lever plates (20), and the at least one lever spacer part (25) are essentially flat plates, which are connected to one another in a formfitting manner.
2. The ratchet wrench according to Claim 1, wherein the ratchet mechanism (44, 4) contains at least two ratchet elements (44), which are each pivotable independently of one another about a separate ratchet axis (46) and are configured to engage in corresponding gear teeth (4) of the output wheel (1).
3. The ratchet wrench according to one of the preceding claims, wherein the ratchet wrench contains a reverse motion lock mechanism (40, 4) acting between the housing (7, 12, 50) and the output wheel (1).
4. The ratchet wrench according to Claim 3, wherein the reverse motion lock mechanism (40, 4) contains at least two pawl elements (40), which are each pivotable independently of one another about a separate pawl axis (42) and are configured to engage in corresponding gear teeth (4) of the output wheel (1).
5. The ratchet wrench according to any one of preceding Claims 2 to 4, wherein at least two ratchet elements (44) and/or at least two pawl elements (40) are configured for the mutual transmission of forces and/or torques by direct mutual mechanical contact.
6. The ratchet wrench according to any one of Claims 2 to 5, wherein at least one of the ratchet elements (44) and/or at least one of the pawl elements (40) is pressed by a spring element (47, 43) against the output wheel (1).
7. The ratchet wrench according to Claim 5 or 6, wherein a group consisting of at least two ratchet elements (44) and/or at least two pawl elements (40) is pressed by a shared spring element (47, 43) against the output wheel (1).
8. The ratchet wrench according to Claim 6 or 7, wherein the spring element (47, 43, 143, 147, 247) is implemented as a single-layer or multilayered leaf spring (47, 43, 143, 147, 247) or as a coiled spring (143) and preferably consists of metal.
9. The ratchet wrench according to Claim 8, wherein a housing spacer part (12) is used as a bearing for the at least two pawl elements (40).
10. The ratchet wrench according to Claim 9 and any one of Claims 6 to 8, wherein the one housing spacer part (12) is simultaneously used as a mount and/or support for the spring element (43).
11. The ratchet wrench according to Claim 2, wherein the lever spacer part (25) is used as a bearing for the at least two ratchet elements (44).
12. The ratchet wrench according to any one of the preceding claims, wherein the housing plates (7), the at least one housing spacer part (12, 17), the lever plates (20), and the at least one lever spacer part (25) are connected to one another by means of cylindrical pins (48, 49) and consist of metal.
13. The ratchet wrench according to Claim 9 and/or Claim 11, wherein the ends of the at least two ratchet elements (44) and/or the at least two pawl elements (40) facing away from the output wheel are provided with bearing pins (46, 42), which are mounted so they are pivotable in cylindrical bearing boreholes (26, 13) in the respective spacer part (25, 12), and wherein the overlap angle of the respective bearing bore hole (26, 13) with the respective bearing pin (46, 42) is greater than 190°.
14. The ratchet wrench according to any one of Claims 2 to 13, wherein each of the ratchet elements (44) and/or the pawl elements (40) covers a gear teeth region of the output wheel (1) which is 3° to 25° and preferably 10° to 20°.
15. The ratchet wrench according to one of the preceding claims, wherein the connecting means (30, 36, 20, 44, 4, 1) are designed such that the drive torque and the output torque are oriented in the same direction.

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