Motion converting mechanism (versions)

FIELD: mechanical engineering.

SUBSTANCE: invention can be used in systems with piston, slider and other units. Proposed mechanism has housing, guides 2, slider 3, output shaft 4 with circumferential section 5 of gear rim alternately engaging with two sections 6, 7 of rim (racks) arranged from side of slider 3 with teeth orientated in opposite direction. End working teeth of edges of rim sections 5-7 are made with body truncation surface having at least one bend and orientated with tilting at acute angle by one extremity to surface of point and by other extremity, square to one of end faces. Surface of truncation of tooth body together with cut of top surface on opposite sections 5 and 6 or 5 and 7 of rim is orientated so that corresponding pairs of working teeth are aligned with ridges at insignificant clearance at opposite relative displacement.

EFFECT: reduced level of vibrations, eliminated possibility of wedging.

6 cl, 21 dwg

 

The present invention relates to mechanical engineering, in particular to a device for converting reciprocating motion into rotational and back, and can be used in mechanical systems with piston, personname, silfonnye, membrane, etc. nodes.

In the first embodiment. A known mechanism for converting movement (a device for converting reciprocating motion), comprising a housing with guides (guide), installed them in the RAM (block bilateral Reiki), kinematically connected with the output shaft (shaft) through the three segments of the ring gear (gears and gear racks in dual rail) and alternate interaction cut crown (gear)made on the circumference of the output shaft (shaft), with two pieces of crown (racks), situated on the side of the slide with opposite oriented teeth (AU 1270459; CL F16H 19/04; 84 g), in which the slider is kinematically connected directly with the output shaft and pieces of gear rims are only different radii of curvature. A segment of the ring gear with a radius of curvature equal to infinity, is a upright plot in the form of a toothed rack on the slider.

Feature known mechanism is that turnout terminal fully profiled tooth is s one of the sections of the main track to another, interacting with him, the segment at the appropriate interval teeth are missing (peripheral gear tooth and the portion of the teeth on one end of each rail in bilateral rail); additional teeth (6 and 7), installed outside the above-mentioned track, also not involved in the turnout with the teeth of the main track; the segment of the ring gear on the output shaft is made to the size of the arc along the length thereof dividing surface, less than the size of the arc length, Central angle of 180°that determines increased gaps between the teeth on the phase shift of the ring gear of the output shaft from one to the other segment of the crown, mounted from the side of the slider.

The disadvantage of this mechanism is its unreliability in operation, as mentioned significant end clearance (on the rail, between the plane 5 and the nearest tooth on a piece of turnout teeth (increased) defines high impact stress on the penultimate tooth cut the crown of the output shaft interacting with the tooth nearest the plane 5 of the leading segment of the crown (Reiki) of the slide. The result of this, at least, is to increase the vibration, and the real possibility of the beginning of the reverse stroke of the RAM (for any of the modes with the driving member as the output shaft or slider) before the start of the rotation of the output shaft, i.e. immediately after the th positioning (especially in the case of mode with a leading link - the slider), determines the violation of the procedure of interaction of the teeth of the segment of the crown shaft with end areas of the other pieces of gear rims (gear racks), mainly due to the increased length of the trough between adjacent integral teeth, which leads to jamming of the mechanism.

Known also adopted as a prototype mechanism for converting motion, comprising a housing with guides (bearings and rollers), installed them in the slider (rod), kinematically connected with the output shaft (drive shaft) through the three segments of the ring gear (toothed sector and rack) and alternate interaction cut crown made on the circumference of the output shaft, with two pieces of crown, situated on the side of the slide with opposite oriented teeth (AU 1270459; F16H 19/04; 83 g), in which the slider is kinematically connected directly with the output shaft.

The peculiarity of the above-mentioned mechanism is the fact that the termination of the teeth of the segment gear output shaft is made from a slice of the active surface of the tooth profile (so-called korrigirovanija) along the entire length of the tooth in the form of surfaces of revolution forming direct which is oriented parallel to the axis of the output shaft, and a segment of the ring gear on the output shaft is made with a number of teeth, sum the and angular steps which the arc length of its cutting surface is less than the arc Central angle of 180° to ensure the turnout of the respective teeth of the segments in the areas of overlap in their tracks when the multi-directional movement relative to each other and on the precondition that enforce fixation (positioning) of the slide in the process turnout of these teeth on the phase shift of a segment of a crown, made on the output shaft, from one to the other of the segments of the rims (rails)installed on the slide (see description, column 2, lines 36-43, AU 1270459; F16H 19/04; 83 g).

The disadvantages of the above-mentioned mechanism are increased end gap mode gearing between the teeth with a solid slice of the active surface and the interaction with the adjacent teeth and the condition of its functioning only when there is a separate actuator positioning of the slider at the endpoints of its run-down relative to the housing. At high speeds of rotation of the shaft, typical modes of operation of internal combustion engines, increased mechanical clearances in the interaction of the teeth intended for turnout, determine the increased dynamic loads on the teeth, and consequently, increased vibration and noise. The reality factors inaccuracies forced positioning, inertia during operation of the device the positioning of the slide and the inconsistency with the possibility of positioning was crawling is on at the expense of peripheral teeth of the segments crowns (rails) it determines the inevitability reduce the amplitude of the stroke of the RAM, the resulting wear on the teeth for slicing active surface and, as a consequence, the violation of the procedure of interaction of the teeth when switching from one rail to another. The result is increased vibration due to the increased level of dynamic loads on the teeth and subsequent jamming of the mechanism.

The objective of the invention is to reduce end clearance when the modes gearing and positioning of teeth located in the areas of turnout, as well as reducing the probability of contact of the above-mentioned teeth at relative opposite movement of the opposed-oriented segments of the crowns.

In accordance with the task in a mechanism for converting motion, comprising a housing with a guide that is installed in them slide, kinematically connected with the output shaft through the three segments of the ring gear and with the alternate engagement of a segment of a crown, made on the circumference of the output shaft, with two pieces of crown, situated on the side of the slide with opposite oriented teeth, according to the invention at the tooth ends cut crown on the output shaft and the corresponding teeth of the other two segments in the areas of turnout is made with the surface of the truncation of the body, at least one inflection, obliquely oriented at an acute angle odnoimennomu to the surface the top and the other end is perpendicular to one of the ends, and the surface of the truncated body of the tooth, together with obrascon surface vertex, focus on the teeth of the opposed set of segments of the crown so that when they are opposite relative movement in the area of the turnout corresponding peaks of the teeth is compatible with a slight gap.

In addition, the length of the crown of the output shaft is made in the form of a gear sector arc length between its end teeth on the peripheral points of their angular steps corresponding to at least an arc of a Central angle of 180°and the surface of the body truncation is performed on the penultimate pair of teeth of the extremities of the segments of the ring gear interacting with a piece of the crown of the output shaft so that the length of the cropping surface tops with full height profile of each extreme of the tooth along the length of the ridge is less than the length of the similar surface of the adjacent tooth in the pair.

Each of the segments is made in the form of a block of four identical segments of the ring gear, combined with each other on the ends of the teeth so that the surface of the truncation tel teeth turnout mirror is oriented relative to each another plane alignment of segments in the block.

Inclined end surface of the truncated body of the tooth is made with a few kinks in the form of step March.

Each of the first segment of the ring gear with the surface of the body truncation of teeth made in the form of a package of cuts crowns width, multiple of the step size step March to the width of the package.

Each of the segments of the crown is made in the form of a block of paired segments with helical teeth, combined in the form of a Chevron, and with straight teeth, and on a separate piece of crown made only teeth with the surface of the body truncation or positioning of teeth.

Pieces of gear rims are made with the size of the step angle of the tooth arc separating surface, corresponding to the three standard angular steps, and with the profile of the working surface of the tooth corresponding to a standard step.

Finally, in the plane of movement of the segments of the ring gear of the slide and symmetrically to the longitudinal axis of the latter on its peripheral surfaces mounted on the supporting cross beam, aligned along the length of the additional ring gear and interacting with two supporting rotating rollers, each of which is combined as a unit with the gear and forming a surface of rotation coinciding with the dividing diameter of the latter.

The technical result of the invention is to reduce the level of vibrations and the underlying assumptions of jamming of the mechanism due to the combined surface truncation teeth zones turnout, ensuring the normalization of the mode gear reduction towards the norms of the butt is o gaps between them.

The second option. A known mechanism for converting motion (piston internal combustion engine), comprising a housing with a guide (cylinder 1), installed them in the slider (piston 2), kinematically associated with the output shaft (7), along with other elements (free running mechanism 6 and coaxially to the output shaft 7, the shaft 5), by means of two constantly interacting gear (gear 4) and the length of the ring gear (rail 3), one of which (the toothed rack 3) installed from the side of the slide (on the piston 2) (RF patent 2028480, F02B 75/32, 95 g), in which the output shaft (7) kinematically directly (because of the mechanism of a free stroke 6) is not associated with the slider (piston 2) and pieces of gear rims are only different radii of curvature. A segment of the ring gear with a radius of curvature equal to infinity, is a upright plot in the form of a toothed rack on the slider.

The lack of a mechanism in unnecessary features reliable actuation mechanism of a free motion in modes of rotational speed characteristic of the internal combustion engine (not less than 1.5 Tyson/min), and complicating the construction of the crank mechanism for positioning the slider at the endpoints of its run (the so-called upper and lower dead points of the piston).

Known also adopted as a prototype mechanism the mechanism for converting motion, comprising a housing with guides (bearings and rollers), installed them in the slider (rod), kinematically connected with the output shaft (drive shaft) through the three segments of the ring gear (toothed sector and rack) and alternate interaction cut crown made on the circumference of the output shaft, with two pieces of crown, situated on the side of the slide with opposite oriented teeth (AU 1270459; F16H 19/04; 83 g), in which the slider is kinematically connected directly with the output shaft.

The peculiarity of the above-mentioned mechanism is the fact that the termination of the teeth of the segment gear output shaft is made from a slice of the active surface of the tooth profile (so-called korrigirovanija), in the form of surfaces of revolution forming direct which is oriented parallel to the axis of the output shaft, and a segment of the ring gear on the output shaft is made with a number of teeth, the amount of angular steps which the arc length of its cutting surface is less than the arc Central angle of 180°to ensure the turnout of the respective teeth of the segments in the areas of overlap in their tracks when the multi-directional movement relative to each other and on the precondition that immobility (positioning) of the slide in the process turnout of these teeth on the phase shift of a segment of a crown, made what about on the output shaft, from one to the other of the segments of the rims (rails)installed on the slide (see description, column 2, lines 36-43, AU 1270459; F16H 19/04; 83 g).

The disadvantages of the above-mentioned mechanism are increased end gap mode gearing between the teeth with a solid slice of the active surface and the interaction with the adjacent teeth and the condition of its functioning only when there is a separate actuator positioning of the slider at the endpoints of its run-down relative to the housing. At high speeds of rotation of the shaft, typical modes of operation of internal combustion engines, increased mechanical clearances in the interaction of the teeth intended for turnout, determine the increased dynamic loads on the teeth, and consequently, increased vibration and noise. The reality factors inaccuracies forced positioning, inertia during operation of the device the positioning of the slide and the inconsistency with the possibility of positioning the slider at the expense of peripheral teeth of the segments crowns (rails) it determines the inevitability reduce the amplitude of the stroke of the slide, resulting in wear of the teeth of the sections of the active surface and, as a consequence, the violation of the procedure of interaction of the teeth when switching from one rail to another. The result is enhanced vibration due to the increased level, the dynamic loads on the teeth and subsequent jamming of the mechanism.

The objective of the invention is to reduce end clearance when the modes gearing and positioning of teeth located in the areas of turnout, as well as reducing the probability of contact of the above-mentioned teeth at relative opposite movement of the opposed-oriented segments of the crowns.

In accordance with the task in a mechanism for converting motion, comprising a housing with a guide that is installed in them slide, kinematically connected with the output shaft through the three segments of the ring gear and with the alternate engagement of a segment of a crown, made on the circumference of the output shaft, with two pieces of crown, situated on the side of the slide with opposite oriented teeth, according to the invention at the tooth ends cut crown on the output shaft and the corresponding teeth of the other two segments in the areas of turnout is made with the surface of the truncation of the body, at least one inflection, obliquely oriented at an acute angle to one extremity to the surface vertex and the other end is perpendicular to one of the ends, and the surface of the truncated body of the tooth, together with obrascon surface vertex, focus on the teeth of the opposed set of segments of the crown so that when they are opposite relative displacement is the situation in the zone turnout corresponding peaks of the teeth is compatible with a slight gap, each of the pieces of gear rims, interacting with a piece of the crown of the output shaft, installed on a separate auxiliary shaft kinematically associated permanently, in turn, slide through the gear and the additional segment of the ring gear mounted on the slider.

In addition, the length of the crown of the output shaft is made in the form of a gear sector with the length of the arc on the periphery of the angular steps of the target teeth corresponding to the Central angle of 180°.

Each of the segments is made in the form of a block of four identical segments of the ring gear, combined with each other on the ends of the teeth so that the surface of the truncation tel teeth turnout mirror is oriented relative to each another plane alignment of segments in the block.

Inclined surface of the truncated body of the tooth is made with a few kinks in the form of step March; each segment of the ring gear with the surface of the body truncation of teeth made in the form of a package of cuts crowns width that is a multiple of the step size step March to the width of the package.

Each of the segments of the crown is made in the form of a block of paired segments with helical teeth, combined in the form of a Chevron, and with straight teeth, and on a separate piece of crown made only teeth with the surface of the body truncation or positioning C is be with the latter.

Pieces of gear rims are made with the size of the step angle of the tooth arc dividing the circumference corresponding to three standard angular steps, with the profile of the working surface of the tooth corresponding to a standard step.

Each gear of the slide along the length combined with a support crossmember, interacting with two supporting rotating rollers, in turn, each of which is combined as a unit with the gear and forming a surface of rotation coincident with the dividing diameter of the latter, one from each beam mounted on the corresponding auxiliary shaft.

The technical result of the invention is to reduce the level of vibrations and the underlying assumptions of jamming of the mechanism due to the combined surface truncation teeth zones turnout, ensuring the normalization of the mode gear reduction towards the norms of the end gaps between them.

Both belong to objects of the same type, have the same purpose and provide the same technical result. Thus, to satisfy the requirement of unity of invention.

Analysis of scientific-technical and patent literature have shown that the invention meets the criteria of "novelty" and "significant differences".

Distinguish the global features of the present invention in more detail is set out in the following description in conjunction with the accompanying drawings, where:

figure 1 shows a General view of the mechanism in the first embodiment;

2 shows a view and cross-section of two razmenivayas teeth;

figure 3 presents the scheme of engagement of the segments of the ring gear in the mechanism;

4 shows phase mechanism;

figure 5 shows the design of the gear mechanism;

6 shows an example of block execution of one of the main segments of the crown;

7 has fulfilled the surface of the body truncation of the teeth;

Fig offered the option of batch execution of the main segments of the ring gear;

Fig.9 shows the layout of the different types of teeth on a separate piece of crown;

figure 10 shows a variant with increased profile of the teeth;

11 shows an offloading device of sliding surfaces of the slide;

Fig shows a General view of the mechanism according to the second variant;

Fig given view and cross section of two razmenivayas teeth;

Fig presents the main design cut the crown of the output shaft;

Fig and 16 shows phase mechanism;

Fig reflected the design of the segments of the ring gear mechanism;

Fig has fulfilled the surface of the body truncation of the teeth;

Fig offered the option of batch execution of the main segments of the ring gear;

Fig shows a variant with increased profile of the teeth;

Fig at the Eden device unloading of the guide surfaces of the slide.

In the first embodiment. The mechanism for converting the movement includes a housing 1 (Fig 1) with the guide surfaces 2, installed them in the RAM 3, kinematically connected with the output shaft 4 through the three segments of the ring gear 5-7. In addition, the output shaft 4 is combined with a flywheel (not shown) to optimize the operation of the mechanism, especially in terms of the extreme points of the coast of the slide 3. On the circumference of the output shaft 4 is performed segment 5 of the ring gear with alternate interaction with the other two 6 and 7 pieces of the crown, situated on the side of the slide 3 with opposite oriented teeth. End operating teeth 8-13 edges of segments 5-7 crown is made with the surface 14-15 truncation of the body with one inflection Oh and obliquely oriented at an angle of about 30° (2) one end 15 to the surface 16 of the tooth tip full profile and the opposite end 14 is perpendicular to one of the ends. Surface truncation 14-15 body of the tooth, together with obrascon surface 16 of the top, opposite the installed sections 5 and 6 or 5 and 7 of the crown are oriented so that when they are opposite relative movement of the corresponding pairs of working teeth 8, 10; 8, 12; 9, 11; 9, 13 compatible crests with a slight gap.

Positioning teeth 17-20 (Figure 1), located after the final working Subie the 8-13 at the edges of the segments of the rims 6 and 7 and with working proceture, function as stoppers, because their peripheral procentury c-d are not involved in the interaction with the teeth of the segment of the crown 5 of the output shaft 4. The number of teeth cut crown 5 corresponds to the number of depressions between the positioning teeth 17 and 20, 18 and 19 in the remaining sections 6 and 7 of the crown. Segment 5 (3) of the crown of the output shaft 4 is made in the form of a gear sector arc length of r-r on the periphery of the angular steps of the target teeth corresponding to the Central angle α<180°.

Reglamentos kinematic alignment between pieces of gear rims 5-7 (Figb and 4D) is determined in the position of one of the extreme points of the coast of the slide 3, when the end of the teeth 8 and 9 cut crown 5 is placed in the terminal cavities of the sections 6 and 7 of the toothed crowns of the positioning of the teeth 17 and 18 or 19 and 20.

The mechanism for converting the motion is as follows.

When the leading link in the mechanism is a slider 3 (Figure 1), the segments of the ring gear 6 and 7, mounted on the last and made in the form of Reiki, involved in translational motion, for example, as indicated by the arrow direction A. In the case of interaction of one (6) of the segments of the crown on the slide 3 with a segment of the ring gear 5, the output shaft 4 receives the rotation in the direction indicated by the arrow C. Before final engagement of its end of the working tooth 8 (Figa) matched with the appropriate positioning of the tooth 17 of the segment of the crown 6 of the final work tooth 9 on the opposite the end of the segment 5, due to the presence of surface 14-15 (Figure 2) truncation his body begins to razminayutsya with the respective opposed working tooth 11, similar on the surface truncation of the body, while the opposite movement relative to the segment of the ring gear 7 to log in to contact with his positioning tooth 18. Simultaneous contact by pairs of teeth 8 17 9 18 (Figb) determine the moment of positioning (fixing) of the slide in a defined end position of its run in one direction relative to the housing 1.

Then the tooth 9 (Pigv), continuing the rotation in the same direction by inertia with the help of the flywheel, overtaken by the tooth 11 and begins to work in normal engagement with the teeth 11 of the segment of the crown 7 after the start of movement of the slide (not shown) in the opposite direction and, as pushing in pair 9, 11 tooth 11 cut crown 7, the output shaft 4 rotates in the same direction Century. At the same time, the tooth 8 of the segment of the crown 5 is withdrawn from contact with the positioning tooth 17 and due to the presence of surface 14-15 (2) truncation of his body starts razminayutsya with the corresponding opposing tooth 10, similar on the surface truncation of the body, while the opposite movement relative to the segment of the ring gear 6 (Pigv) and exits from the zone of interaction with the latter.

Turning next segment of the ring gear 5 (Figg its target tooth 8 is W is in the finish the interaction with the positioning tooth 19 on the segment 7 of the crown, thus terminal tooth 9 due to the presence of surface 14-15 (2) truncation of the body begins to razminayutsya with the corresponding opposing tooth 13 (High), similar to the surface of the truncation of the body in opposite relative movement before entering in contact with his positioning tooth 20. Following this simultaneous contact of the teeth 9, 20, 8, 19 (Figd) determine the moment of positioning (stop) of the slide in the opposite extreme position of its run in the other direction relative to the housing. Then the tooth 9 (Fige),), continuing the rotation in the same direction by inertia with the help of the flywheel, overtaken by the tooth 13 and begins to work in normal engagement after the start of movement of the slide again in the direction a and, as pushing in pair 9, 13 is the 13 tooth cut crown 6, the length of the crown 5 on the output shaft 4 will continue the rotation in the normal direction of the Century. At the same time, the tooth 8 is withdrawn from contact with the positioning tooth 19 and due to the presence of surface 14-15 (Figure 2) truncation his body begins to razminayutsya with the corresponding opposing tooth 12 (Fige), similar to the surface of the truncation of the body, while the opposite movement relative to the segment of the ring gear 7 and exits from the zone of interaction with the latter. Further, the alternating interaction of a segment of the ring gear 5 pieces of gear rims 6 and 7 of the slide 3 is storaetsa in the above order.

When the leading link in the mechanism is the output shaft 4 with a segment of the ring gear 5, rotating in the indicated arrow direction, the order of interaction with the last pieces of gear rims 6 and 7 differ only by the fact that after phase positioning in the primary interacting pairs with different composition of 9, 18 (Pigv) or 9, 20 (Pigd) is already pushing the tooth 9 of the segment of the crown 5 of the output shaft 4.

Thus, when the opposite relative movement of the opposed-oriented segments of the crown of the teeth with the surface of the trimming bodies diverge without mutual contact their tops, and in following the movement of interacting mentioned teeth ensures the normal mode gear.

The capacity of the proposed mechanism for converting reciprocating motion into rotational and back (Figure 4), i.e. the rotary to reciprocating, functional elements of the same links logically compatible with the mode of operation of internal combustion engines, when in the position of so-called extreme points rundown of the piston (slider) function leading link assumes the crankshaft (output shaft) at the time of a change in the direction of movement of the piston (slider).

In addition, for greater normalization values end clearance between the teeth zones turnout OTP is ZOK 5 (5) of the crown of the output shaft 4 is made in the form of a gear sector arc length of r-r between the end teeth on the peripheral points of the angular step m acorresponding to at least an arc of a Central angle of 180°and the surface of the body truncation 14-15 (figure 2) can be performed on the penultimate pair of teeth 10, 21 11, 22, 12, 23 13, 24 (5) the ends of the segments 6, 7 gear interacting with a segment 5 of the crown so that the length of the cropping surface 16 tops with full height profile of each extreme of the tooth along the length of the ridge is less than the length of the similar surface of the adjacent tooth in the pair.

Several identical pieces of gear rims, for example four (6)can be performed with a combination between the ends of the teeth so that the surface 14-15 truncation of their bodies and trimming the surface 16 of the vertex mirror is oriented relative to each another plane n1-n1n2-n2,... na-nacombining the segments into a single block F, and f established similar unit G combined on the same level areas 16 scraps surfaces of the tops of the teeth 8 to 13 are stacked on the corresponding ends of the surfaces 14 truncation tel teeth.

Inclined surface 15 (Fig 1) truncation of the body of the tooth, in turn, can be accomplished with a few kinks (7) in the form of step March.

Each segment of the ring gear with the surface of the body truncation working on the teeth may be the made in the form of a package (Fig) of the segments of the rims width, a multiple of, for example, the step size step March to the width of the package. Each ledge d1d2dastep draft tooth on the surface of the body truncation is actually the top of the narrowed width of the crown and the stripped-down, except the first ledge with poverhnosti 16 at one of the ends, up to a certain height of the working of the tooth, which in normal gear (interacting teeth are moved in one direction) is shorter section of his work path in contact with the working area of the contour of the corresponding ledge interacting opposing tooth. Thus, the sequential interaction of the respective opposed pairs of ledges on their particular section of the profile creates the condition of continuity of contact between each pair of teeth with an area of truncation of the profile in the area of working relations.

Each segment of the ring gear shown, for example, schematically in figures 9 and conventionally in the form deployed in the plane of the rack may be made in the form of the block parallel to the paired segments with helical teeth 25, combined in the form of a Chevron, and on a separate segment with 26 straight teeth made only working teeth with the surface of the body truncation or positioning of the teeth and the last. The combined set of teeth on the segments of the vents is to provide a lower dynamic load on the remaining workers teeth outside of the turnout.

To improve the reliability of the main gearing mechanism segments 5-7 (Figure 10) teeth, crowns can be made with the size of the step angle M of the tooth arc dividing the circumference corresponding to the three standard steps m, with a profile of the working surface of the tooth corresponding standard step m.

In the plane of movement of the segments 6 and 7 (11) of the ring gear of the slide 3 and symmetrically to the longitudinal axis of the latter on its peripheral surfaces can be installed on the supporting cross beam 27 and 28, the combined length with an additional ring gear in the form of a toothed rack 29, 30 and interacting with the two anchor swivel axes of the rollers 31 and 32, each of which is combined as a unit with the gear 33 and forming a surface of rotation coinciding with the dividing diameter of the latter. Additional guides rolling bearings 31 and 32 provide the reduction partyrausch loads between the guide surfaces of the housing 1 and the slider 3 from the reactions of interaction gears on the latter.

Finally, in addition to gearing can be applied, for example, zamochnoe engaged.

The second option. The mechanism for converting the movement includes a housing 1 (Fig) with the guides 2, installed them in the RAM 3, kinematically connected with the output shaft 4 in a row with a friend who mi links, through the three segments of the ring gear 5-7. In addition, the output shaft 4 is combined with a flywheel (not shown) to optimize the operation of the mechanism, especially in terms of the extreme points of the coast of the slide 3. On the circumference of the output shaft 4 is performed segment 5 of the ring gear with alternate interaction with the other two 6 and 7 pieces of the crown, each of which is placed on a separate auxiliary shaft 34, 35, and with opposite oriented teeth. End operating teeth 8-13 edges of segments 5-7 crown is made with the surface of the body truncation 14-15 with one inflection Oh, obliquely oriented at an angle of about 30° (Fig) one end 15 to the surface 16 of the top working full tooth profile and the opposite end 14 is perpendicular to one of the ends. Surface truncation 14-15 body of the tooth, together with obrascon surface 16 of the top, in the form of a comb tooth opposite the installed sections 5 and 6 or 5 and 7 of the crown are oriented so that when they are opposite relative movement of the corresponding pairs of working teeth 8, 10; 8, 12; 9, 11; 9, 13 on the surface truncation tel 14-15 and cutting surface 16 of the tooth tip is oriented in such a way that is compatible with a slight gap.

Positioning teeth 17-20 (Fig)located after the final working 8-13 teeth at the edges of the segments of venzo the 6 and 7 and with working proceture, function as stoppers, because their peripheral procentury c-d are not involved in the interaction with the teeth of the segment of the crown 5 of the output shaft 4. The number of teeth cut crown 5 corresponds to the number of depressions between the positioning teeth 17 and 20, 18 and 19 in the remaining sections 6 and 7 of the crown. Each of the supporting shafts 34, 35, in turn, kinematically connected directly to the RAM 3 through the constant interaction of the gear 36 and the relevant additional cut crown, made in the form of a toothed rack 37. Segment 5 (Fig) crown of the output shaft 4 is made in the form of a gear sector arc length of r-r on the periphery of the angular steps of the target teeth corresponding to the Central angle α<180°.

Reglamentos kinematic alignment between pieces of gear rims 5-7 is determined in the position of one of the extreme points of the coast of the slide 3, when the end of the teeth 8 and 9 (Figb and 16B) cut the crown 5 is placed in the terminal cavities of the sections 6 and 7 of the toothed crowns of the positioning of the teeth 17 and 18 or 19 and 20.

The mechanism for converting the motion is as follows.

When the leading link in the mechanism is a slider 3 (Fig), the rack 37, mounted on the latter, involved in translational motion, for example, as indicated by the arrow a, and through the appropriate the stubble 36, respectively mounted on the supporting shafts 34 and 35 pieces of gear rims 6, 7 starts rotating in opposite directions and With°. In the case of interaction of one (6) of the segments of the crown (6, 7) with a segment of the ring gear 5, the output shaft 4 starts to rotate in the direction indicated by the arrow In, and before final engagement of its end of the working tooth 8 (Figa) with the corresponding positioning tooth 17, the final work tooth 9 on the opposite end of the segment 5 due to the presence of surface 14-15 (Fig) truncation his body begins razminovicha with the respective opposed working tooth 11 (Figa), similar to the surface of the truncation of the body, while the opposite movement relative to the segment of the ring gear 7 to log in to contact with his positioning tooth 18. Simultaneous contact by pairs of teeth 8 teeth 17 and 9 tooth 18 (Figb) determine the moment of positioning (stop) of the slide in a defined end position of its run in one direction relative to the body.

Then the tooth 9 (Pigv), continuing the rotation in the same direction by inertia with the help of the flywheel, overtaken by the tooth 11 and begins to work in normal engagement with the teeth 11 of the segment of the crown 7 after the start of movement of the slide (not shown) in the opposite direction and, as pushing in pair 9, 11 tooth 11 cut crown 7, the output of the second shaft 4 rotates in the same direction C. At the same time, the tooth 8 of the segment of the crown 5 is withdrawn from contact with the positioning tooth 17 and due to the presence of surface 14-15 (Fig) truncation his body begins to razminayutsya with the respective opposed working tooth 10, similar on the surface truncation of the body, while the opposite movement relative to the segment of the ring gear 6 (Pigv) and exits from the zone of interaction with the latter.

Turning next segment of the ring gear 5 (Figa its target work tooth 8 is now in the finishing engagement with the positioning teeth 19 on the segment 7 of the crown, with the target tooth 9 due to the presence of surface 14-15 truncation body begins to razminayutsya with the respective opposed working tooth 13, similar on the surface truncation of the body in opposite relative movement before entering in contact with his positioning tooth 20. Following this simultaneous contact of the teeth 9, 20, 8, 19 (Figb) determine the moment of positioning (stop) of the slide in the opposite extreme position of its run in the other direction relative to the housing. Then the tooth 9 (Pigv), continuing the rotation in the same direction by inertia with the help of the flywheel, overtaken by the tooth 13 and begins to work with him in normal engagement after the start of movement of the slide (conventionally not shown) in the opposite direction and, as pushing in the pair , 13 is the working tooth 13 cut crown 6, the length of the crown 5 on the output shaft 4 will continue the rotation in the normal direction of the Century. At the same time working tooth 8 is withdrawn from contact with the positioning tooth 19 and due to the presence of surface 14-15 truncation his body begins to razminayutsya with the respective opposed working tooth 12, similar on the surface truncation of the body, while the opposite movement relative to the segment of the ring gear 7 and exits from the zone of interaction with the latter. Further, the alternating interaction of a segment of the ring gear 5 pieces of gear rims 6 and 7 of the slide 3 is repeated in the above manner.

When the leading link in the mechanism is the output shaft 4 with a segment of the ring gear 5, rotating in the indicated arrow direction, the order of interaction with the last pieces of gear rims 6 and 7 differ only by the fact that after phase positioning in the primary interacting pairs with different composition of 9, 18 (Figb) or 9, 20 (Figb) is already pushing the tooth 9 of the segment of the crown 5 of the output shaft 4.

Thus, when the opposite relative movement of the opposed-oriented segments of the crown of the teeth with the surface of the trimming bodies diverge without mutual contact their tops, and in following the movement of interacting mentioned teeth is normal the capacity mode gear.

The capacity of the proposed mechanism for converting reciprocating motion into rotational and back (Fig-16), i.e. the rotary to reciprocating, functional elements of the same links logically compatible with the mode of operation of internal combustion engines, when in the position of so-called extreme points rundown of the piston (slider) function leading link assumes the crankshaft (output shaft) at the time of a change in the direction of movement of the piston (slider).

In addition, for greater normalization values end clearance between the teeth zones turnout segment 5 (Fig) crown of the output shaft 4 is made in the form of a gear sector arc length of r-r between the end teeth on the peripheral points of the angular step m corresponding to at least an arc of a Central angle of 180°.

Several identical pieces of gear rims, for example four (6)can be performed with a combination between the ends of the teeth so that the surface 14-15 truncation of their bodies and the surface 16 of scraps of vertices mirror is oriented relative to each another plane n1-n1n2-n2,... na-nacombining the segments into a single block F, and f established similar unit G combined on the same level areas 16 scraps surfaces of the tops of the servant of the rest of the teeth 8 to 13 are stacked on the corresponding ends 14 truncation surfaces, oriented perpendicular to the end faces of the combined working of teeth.

Inclined surface 15 (Fig) truncation of the body of the tooth can be done with a few kinks (Fig) in the form of step March.

Each segment of the ring gear with the surface of the body truncation working on the teeth can be made in the form of a package (Fig) of the segments of the rims with a width that is a multiple of, for example, the step size step March to the width of the package. Each ledge d1d2dastep draft tooth on the surface of the body truncation is actually the top of the narrowed width of the crown and the stripped-down, in addition to the initial ledge 16 at one of the ends, up to a certain height of the working of the tooth, which in normal gear (interacting teeth are moved in one direction) is shorter section of his work path in contact with the working area of the contour of the corresponding ledge interacting opposing tooth. Thus, the sequential interaction of the respective opposed pairs of ledges on their particular section of the profile creates the condition of continuity of contact between each pair of teeth with an area of truncation of the profile in the area of working relations.

Each segment of the ring gear shown, for example, schematically in figures 9 and conventionally in the form deployed in flat the minute rack, can be made in the form of the block parallel to the paired segments with helical teeth 25, combined in the form of a Chevron, and on a separate segment with 26 straight teeth made only working teeth with the surface of the body truncation or positioning of the teeth and the last. The combined set of teeth on the segments crowns provide a lower dynamic load on the remaining workers teeth outside of the turnout.

To improve the reliability of the main gearing mechanism segments 5-7 (Fig) teeth, crowns can be made with the size of the step angle M of the tooth arc dividing the circumference corresponding to the three standard steps m, with a profile of the working surface of the tooth corresponding standard step m.

Each toothed rack 37 (Fig) of the RAM 3 by the length can be combined with individual support crossmember 27, 28 interacting simultaneously with two supporting rotating rollers 31, 32, each of which is combined as a unit with the gear 36, 38 and forming a surface of rotation coincident with the dividing diameter of the latter, one of which 36 from the side of each beam 27, 28 are mounted on the corresponding auxiliary shaft 34, 35. Additional guides rolling bearings 31 and 32 provide the reduction partyrausch loads between the guide surfaces of the building is a 1 and the slider 3 from the reactions of interaction gears on the latter.

Finally, in addition to gearing can be applied, for example, zamochnoe engaged.

The technical result of the invention is to reduce the level of vibrations and the underlying assumptions of jamming of the mechanism.

The use of the proposed invention provides a high reliability of the conversion movement, as the teeth turnout performed with a combined surface truncation of the body, which virtually eliminates contact the tops of the opposed teeth upon opposite relative movement in the area of the turnout without using an additional actuator fixing of the slide, and ensure the normalization of the mode gear associated with the movement of the interacting teeth turnout and the adjacent neighboring teeth on opposite oriented segments of the crowns.

1. The mechanism for converting motion, comprising a housing with a guide that is installed in them slide, kinematically connected with the output shaft through the three segments of the ring gear, with the possibility of sequential interaction of a segment of a crown, made on the circumference of the output shaft, with two pieces of crown, situated on the side of the slide with opposite oriented teeth, characterized in that at the tooth ends cut crown on o the bottom of the shaft and, at least, the last tooth of each periphery of the other of the two segments is made with the surface of the truncated body with at least one inflection, obliquely oriented at an acute angle to one extremity to the surface vertex and the other end is perpendicular to one of the ends, and the surface of the body truncation of the tooth together with obrascon peaks along the ridge, is focused on the teeth of the opposed set of segments of the crown so that when they are opposite relative movement in the area of the turnout peaks mentioned teeth combined with a slight gap.

2. The mechanism according to claim 1, characterized in that the inclined portion of the surface of the truncated body of the tooth is made with a few kinks in the form of step March.

3. The mechanism according to claim 1 or 2, characterized in that the surface of the body truncation performed two penultimate tooth portions of the segments of the toothed crowns, interacting with cut crown on the output shaft.

4. The mechanism for converting motion, comprising a housing with a guide that is installed in them slide, kinematically connected with the output shaft through the three segments of the ring gear by the alternate engagement of a segment of a crown, made on the circumference of the output shaft, with the other two pieces of the crown, situated on the side of the slide with the op is osito oriented teeth, characterized in that at the tooth ends cut crown on the output shaft and the second to last tooth of each periphery of the other of the two segments is made with the surface of the truncated body with at least one inflection, obliquely oriented at an acute angle to one extremity to the surface vertex and the other end is perpendicular to one of the ends, and the surface of the body truncation of the tooth together with obrascon peaks along the ridge, is focused on the teeth of the opposed set of segments of the crown so that when they are opposite relative movement in the area of the turnout peaks mentioned teeth combined with a slight gap, and each of these pieces of gear rims, interactive to cut the crown of the output shaft, in turn, kinematically connected with the slide by means of a separate auxiliary shaft.

5. The mechanism according to claim 4, characterized in that the inclined portion of the surface of the truncated body of the tooth is made with a few kinks in the form of step March.

6. The mechanism according to claim 4 or 5, characterized in that segment of the crown of the output shaft is made in the form of a gear sector arc length between its end teeth on the peripheral points of their angular steps corresponding to at least an arc of a Central angle of 180°.



 

Same patents:

FIELD: mechanical engineering.

SUBSTANCE: invention relates to lever-tooth mechanisms with rack and it can be used to drive mechanisms of slotting machine, automobile windshield wiper, brush cleaner of screens of grain-cleaning machines, in automatic machines, etc. Proposed mechanism contains base, toothed wheel and crank hinge-mounted on base for rotation, and toothed rack engaging with toothed wheel. Lever with guide member is hinge-mounted on axle of toothed wheel. Guide member engages with rear side of toothed rack forming translational pair. Guide member is made in form of roller hinge-mounted for rotation on axle installed on free end of lever provided with thread. Axle of roller is provided with through cross hole to pass threaded end of lever. Roller is held on lever by nuts arranged from outer and inner sides of roller to adjust and fix radial clearance in meshing between rack and toothed wheels.

EFFECT: improved operating characteristics of mechanism.

2 dwg

Motion converter // 2308603

FIELD: mechanical engineering, particularly combustion engines, pumps and positive displacement compressors, namely mechanisms, which covert reciprocal movement into rotation and vice versa.

SUBSTANCE: motion converter comprises four cylinders grouped in pairs. Pistons of opposite cylinders are connected with each other through fixed bar. The converter has the first and the second pair of fixedly connected parallel toothed racks brought into engagement with corresponding segmental gear-wheels fixedly connected to one output shaft. In each segmented gear-wheel teeth extend for less than half of 180° pitch circle. Segmented gear-wheels cooperating with corresponding toothed racks are shifted through predetermined angle, preferably 90° angle, one relatively another.

EFFECT: increased performance.

3 cl, 5 dwg, 1 tbl

FIELD: the invention refers to the field of machine building namely to transformers of alternate/reciprocal motion into rotary and vice-versa and may be used in piston engines, pumps, compressors and other gears.

SUBSTANCE: the transformer is a planetary toothed mechanism consisting of a non-rotating central pinion with inner toothed gearing making alternate/reciprocal motion relatively to the axle rotating together with firmly connected with it from one side and interacting with the central pinion-satellite. The length of the toothed rim of the satellite is two times smaller then the length of the toothed rim of the central pinion, of the link or of the mechanism providing continuous engagement of the teeth of the central pinion and the satellite. The link and the mechanism are fulfilled in such a manner that install marginally allowable distance between the positions of their joining with the central pinion and with the satellite not installing the maximum allowable value of this distance. The central pinion and the satellite have figured different profile according to their toothed rims.

EFFECT: increases the coefficient of efficiency of transformation of the alternate/reciprocal motion into rotary and vice-versa and simplifies the construction of the toothed transformer.

10 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: according to invention, body 10 forms prismatic chamber 12 whose cross section is oval of odd order formed from arcs 34, 36, 38 with first smaller radius of curvature and arcs 40, 42, 44 with second, larger radius of curvature changing continuously and differentially one into the other. Thus, corresponding cylindrical parts of inner surface of chamber are formed. Chamber 12 accommodates rotating piston 60 whose cross section forms oval of the order smaller by 1 than order of chamber 12. Opposite parts of side surface are formed on rotating piston 60, one of which rotates in part of inner surface of radius of curvature equal to said part and the other adjoins opposite part of inner surface to slide along surface. rotating piston 60 divides chamber 12 in any position into two working spaces 78, 80. Instantaneous axes of rotation 112, 114 of rotating piston 60 are determined on middle plane of piston being fixed for a short time. Working agent to set rotating piston 60 into motion is periodically introduced into working spaces. Rotating piston 60 rotates in each phase of its motion in one of opposite parts of its side surface 70 in corresponding part of inner side surface 62 of chamber around corresponding instantaneous axis of rotation 112 and slides by opposite part of its surface 72 along corresponding opposite part of inner side surface 54 of chamber 12 to stop, i.e. until it comes into extreme position. Then, to execute following phase of movement, instantaneous axis of rotation jumps from previous position into second possible position 114 relative to piston and is fixed in this position for a short rime. Driven or driving shaft 102 is in engagement with rotating piston 60. To prevent kinematic ambiguity of instantaneous axis of rotation in extreme position, instantaneous axis of rotation is mechanically fixed in each extreme position for a time (Fig.1).

EFFECT: improved efficiency of machine in operation.

20 cl, 79 dwg

Gearing device // 2289046

FIELD: mechanical engineering.

SUBSTANCE: gearing device comprises two gear racks and gear wheel. The recess is provided between the racks (26) and (28) to prevent gear wheel (10) against the contact with both of the racks simultaneously. The adapting gear member between two racks is defined by the convex gear arc. When gear wheel (10) engages adapting member (30), it disengages rack (26) immediately before the moment when it engages rack (28).

EFFECT: improved structure.

13 cl

FIELD: mechanical engineering.

SUBSTANCE: gear converter comprises nonrotating shaped gear wheel (1) with inner teeth engagement, which reciprocates with respect to semiaxle (3) that rotates together with shaped pinion (2) secured to the semiaxle from one side and cooperating with shaped gear wheel (1). The length of the gear rim of pinion (2) is twice as less as that of gear rim of shaped gear wheel (1). The continuous engagement of the teeth of shaped gear wheel (1) with pinion (2) is provided by means of the cooperation of cam (4) that is connected with pinion (2) with roller (8) freely rotating around its axis (9).

EFFECT: enhanced efficiency.

7 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: converter comprises the rack, gearing, output shaft, two overloading clutches, and thrusts. The rack connected with the pivot is in coincidence with the overrunning clutches which are in a staggered contact with conical gears. The movement of the conical pivots are limited by means of the pinion secured to the output shaft. The racks provided with the gearing and overrunning clutches are interposed between the two conical gearings.

EFFECT: simplified structure.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: device comprises rack, gears, output shaft, two overrunning clutches, and stops. The output shaft is inclined at an angle of 90° to the driving shaft. The gear engaging the rack is pivotally connected with the driving shaft. The faces of the gear abut against two overrunning clutches which are in a contact with the stop and conical gear pivotally mounted on the driving shaft. The conical gear is connected with the intermediate pinion secured to the output shaft. The intermediate pinion engages the conical gear secured to the driving shaft. The additional stop is secured to the shaft, set in the gear actuated by the rack, and housed by the flange. The device also has roller for keeping the space in the rack-gear engagement constant.

EFFECT: simplified assembling.

3 cl, 1 dwg

FIELD: mechanical engineering.

SUBSTANCE: gearing converter comprises single gearing frame with inner or outer gear cut, two gearing racks (5) and (16) whose ends are interconnected via intermediate sections that define smooth members for power pinion (13) from one gear rack to the other, locking roller (14) that rolls over the shaped surface, one driving rod (1), carrier (15) with locking roller (14) connected with the gear rack and mounted on power shaft (4), and power pinion (13). The intermediate sections of the gear frame are provided with rounds that are redial with respect to the axis of rotation of the gear rack.

EFFECT: expanded functional capabilities.

16 cl, 9 dwg

FIELD: mechanical engineering.

SUBSTANCE: planet gearing mechanism comprises shaped gear rack (9), base (1) with guides for longitudinal movements of the rack, rotatable lever (5) with gear wheel (4), and driving gear wheel (10). Shaped rack (9) has guides with flat (7) and profiled surfaces (2) and (8). The axis of rotation of wheel (10) passes through shaped rack (9), is in coincidence with the axis of rotation of lever (5), and transmits motion to shaped rack (9) through gear wheel (4) of rotatable lever (5). Rotatable lever (5) has bearings (3) and (6) which move individually over flat (7) and profiled (2) and (8) surfaces of rack (9).

EFFECT: simplified structure.

2 dwg

FIELD: mechanical engineering.

SUBSTANCE: planet gearing mechanism comprises shaped gear rack (9), base (1) with guides for longitudinal movements of the rack, rotatable lever (5) with gear wheel (4), and driving gear wheel (10). Shaped rack (9) has guides with flat (7) and profiled surfaces (2) and (8). The axis of rotation of wheel (10) passes through shaped rack (9), is in coincidence with the axis of rotation of lever (5), and transmits motion to shaped rack (9) through gear wheel (4) of rotatable lever (5). Rotatable lever (5) has bearings (3) and (6) which move individually over flat (7) and profiled (2) and (8) surfaces of rack (9).

EFFECT: simplified structure.

2 dwg

FIELD: mechanical engineering.

SUBSTANCE: gearing converter comprises single gearing frame with inner or outer gear cut, two gearing racks (5) and (16) whose ends are interconnected via intermediate sections that define smooth members for power pinion (13) from one gear rack to the other, locking roller (14) that rolls over the shaped surface, one driving rod (1), carrier (15) with locking roller (14) connected with the gear rack and mounted on power shaft (4), and power pinion (13). The intermediate sections of the gear frame are provided with rounds that are redial with respect to the axis of rotation of the gear rack.

EFFECT: expanded functional capabilities.

16 cl, 9 dwg

FIELD: mechanical engineering.

SUBSTANCE: device comprises rack, gears, output shaft, two overrunning clutches, and stops. The output shaft is inclined at an angle of 90° to the driving shaft. The gear engaging the rack is pivotally connected with the driving shaft. The faces of the gear abut against two overrunning clutches which are in a contact with the stop and conical gear pivotally mounted on the driving shaft. The conical gear is connected with the intermediate pinion secured to the output shaft. The intermediate pinion engages the conical gear secured to the driving shaft. The additional stop is secured to the shaft, set in the gear actuated by the rack, and housed by the flange. The device also has roller for keeping the space in the rack-gear engagement constant.

EFFECT: simplified assembling.

3 cl, 1 dwg

FIELD: mechanical engineering.

SUBSTANCE: converter comprises the rack, gearing, output shaft, two overloading clutches, and thrusts. The rack connected with the pivot is in coincidence with the overrunning clutches which are in a staggered contact with conical gears. The movement of the conical pivots are limited by means of the pinion secured to the output shaft. The racks provided with the gearing and overrunning clutches are interposed between the two conical gearings.

EFFECT: simplified structure.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: gear converter comprises nonrotating shaped gear wheel (1) with inner teeth engagement, which reciprocates with respect to semiaxle (3) that rotates together with shaped pinion (2) secured to the semiaxle from one side and cooperating with shaped gear wheel (1). The length of the gear rim of pinion (2) is twice as less as that of gear rim of shaped gear wheel (1). The continuous engagement of the teeth of shaped gear wheel (1) with pinion (2) is provided by means of the cooperation of cam (4) that is connected with pinion (2) with roller (8) freely rotating around its axis (9).

EFFECT: enhanced efficiency.

7 cl, 6 dwg

Gearing device // 2289046

FIELD: mechanical engineering.

SUBSTANCE: gearing device comprises two gear racks and gear wheel. The recess is provided between the racks (26) and (28) to prevent gear wheel (10) against the contact with both of the racks simultaneously. The adapting gear member between two racks is defined by the convex gear arc. When gear wheel (10) engages adapting member (30), it disengages rack (26) immediately before the moment when it engages rack (28).

EFFECT: improved structure.

13 cl

FIELD: mechanical engineering.

SUBSTANCE: according to invention, body 10 forms prismatic chamber 12 whose cross section is oval of odd order formed from arcs 34, 36, 38 with first smaller radius of curvature and arcs 40, 42, 44 with second, larger radius of curvature changing continuously and differentially one into the other. Thus, corresponding cylindrical parts of inner surface of chamber are formed. Chamber 12 accommodates rotating piston 60 whose cross section forms oval of the order smaller by 1 than order of chamber 12. Opposite parts of side surface are formed on rotating piston 60, one of which rotates in part of inner surface of radius of curvature equal to said part and the other adjoins opposite part of inner surface to slide along surface. rotating piston 60 divides chamber 12 in any position into two working spaces 78, 80. Instantaneous axes of rotation 112, 114 of rotating piston 60 are determined on middle plane of piston being fixed for a short time. Working agent to set rotating piston 60 into motion is periodically introduced into working spaces. Rotating piston 60 rotates in each phase of its motion in one of opposite parts of its side surface 70 in corresponding part of inner side surface 62 of chamber around corresponding instantaneous axis of rotation 112 and slides by opposite part of its surface 72 along corresponding opposite part of inner side surface 54 of chamber 12 to stop, i.e. until it comes into extreme position. Then, to execute following phase of movement, instantaneous axis of rotation jumps from previous position into second possible position 114 relative to piston and is fixed in this position for a short rime. Driven or driving shaft 102 is in engagement with rotating piston 60. To prevent kinematic ambiguity of instantaneous axis of rotation in extreme position, instantaneous axis of rotation is mechanically fixed in each extreme position for a time (Fig.1).

EFFECT: improved efficiency of machine in operation.

20 cl, 79 dwg

FIELD: the invention refers to the field of machine building namely to transformers of alternate/reciprocal motion into rotary and vice-versa and may be used in piston engines, pumps, compressors and other gears.

SUBSTANCE: the transformer is a planetary toothed mechanism consisting of a non-rotating central pinion with inner toothed gearing making alternate/reciprocal motion relatively to the axle rotating together with firmly connected with it from one side and interacting with the central pinion-satellite. The length of the toothed rim of the satellite is two times smaller then the length of the toothed rim of the central pinion, of the link or of the mechanism providing continuous engagement of the teeth of the central pinion and the satellite. The link and the mechanism are fulfilled in such a manner that install marginally allowable distance between the positions of their joining with the central pinion and with the satellite not installing the maximum allowable value of this distance. The central pinion and the satellite have figured different profile according to their toothed rims.

EFFECT: increases the coefficient of efficiency of transformation of the alternate/reciprocal motion into rotary and vice-versa and simplifies the construction of the toothed transformer.

10 cl, 6 dwg

Motion converter // 2308603

FIELD: mechanical engineering, particularly combustion engines, pumps and positive displacement compressors, namely mechanisms, which covert reciprocal movement into rotation and vice versa.

SUBSTANCE: motion converter comprises four cylinders grouped in pairs. Pistons of opposite cylinders are connected with each other through fixed bar. The converter has the first and the second pair of fixedly connected parallel toothed racks brought into engagement with corresponding segmental gear-wheels fixedly connected to one output shaft. In each segmented gear-wheel teeth extend for less than half of 180° pitch circle. Segmented gear-wheels cooperating with corresponding toothed racks are shifted through predetermined angle, preferably 90° angle, one relatively another.

EFFECT: increased performance.

3 cl, 5 dwg, 1 tbl

FIELD: mechanical engineering.

SUBSTANCE: invention relates to lever-tooth mechanisms with rack and it can be used to drive mechanisms of slotting machine, automobile windshield wiper, brush cleaner of screens of grain-cleaning machines, in automatic machines, etc. Proposed mechanism contains base, toothed wheel and crank hinge-mounted on base for rotation, and toothed rack engaging with toothed wheel. Lever with guide member is hinge-mounted on axle of toothed wheel. Guide member engages with rear side of toothed rack forming translational pair. Guide member is made in form of roller hinge-mounted for rotation on axle installed on free end of lever provided with thread. Axle of roller is provided with through cross hole to pass threaded end of lever. Roller is held on lever by nuts arranged from outer and inner sides of roller to adjust and fix radial clearance in meshing between rack and toothed wheels.

EFFECT: improved operating characteristics of mechanism.

2 dwg

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