• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    SUMMARY The invention relates to a gear configuration (|; ll; ll ') of scissors type comprising a first gear (10; 60) and a second gear (30; 70) arranged coaxially with and rotatably relative to said first gear (10; 60). said gears are arranged to cooperate together with an additional gear in a transmission configuration. a position where said first and second gears (10; 60, 30; 70) differ from each other from said engaging position. The invention also relates to a transmission configuration. The invention also relates to an engine. (Fig. Zb)
    公开号:SE1051012A1
    申请号:SE1051012
    申请日:2010-09-30
    公开日:2012-03-31
    发明作者:Thorbjoern Hansen；Stefan Fors
    申请人:Scania Cv Ab；
    IPC主号:
    专利说明:

    OBJECT OF THE INVENTION An object of the present invention is to provide a gear type of scissor type which in operation reduces noise caused by gear engagement with another gear which does not require complicated interventions for the scissor function to function where the gear configuration in mounted position is difficult to access.
    A further object of the present invention is to provide a scissor-type gear configuration which facilitates mounting thereof in a transmission configuration. SUMMARY OF THE INVENTION This and other objects set forth in the following description are accomplished by a gear configuration, a transmission configuration and a motor configuration. and further having the features set forth in the characterizing part of appended independent claims 1, 17 and 18. Preferred embodiments of the gear configuration are defined in appended dependent claims 2-16.
    According to the invention, the object is achieved with a scissor-type gear configuration comprising a first gear and a second gear arranged coaxially with and rotatably relative to said first gear, said gears being arranged to co-operate with a further gear in a transmission configuration and said second gear being arranged to be mutually rotatably arranged against a spring force in an engaging position with said further gears, said first and second gears being arranged to rotatably assume a position in a mounting position mutually spring-loaded rotatably, said first and second gears deviating from said engaging position. This makes it possible to use the additional gear to provide the engaging position so that the scissor function of the gear configuration functions without any further engagement in the engaging position. Furthermore, assembly is facilitated.
    According to an embodiment of the gear configuration, said first and second gears in said mounting position are arranged to deviate by a predetermined angle of rotation from said engaging position and this position corresponds to a predetermined prestressing spring load where said first and second gears prevent a minor spring from than said predetermined biasing spring load. This enables simple assembly and bringing into engagement of said further gears, whereby the desired bias is obtained in the engaging position, whereby the desired shear function of the gear configuration is achieved.
    According to one embodiment, the gear configuration comprises a stop configuration arranged to prevent the intake of a position corresponding to a biasing spring load less than said predetermined biasing spring load. This enables simple assembly and bringing into engagement of said further gears, whereby the desired bias is obtained in the engaging position, whereby the desired shear function of the gear configuration is achieved.
    According to an embodiment of the gear configuration, said first and second gears in said engaging position are arranged to assume a position where said biasing spring load is greater than said predetermined biasing spring load and where the deviation is less than in the mounting position. This avoids that the mounting position at the scissor function is reached in the engaging position, which means that the scissor function of the gear configuration will function undisturbed, which results in good noise reduction. According to an embodiment of the gear configuration, said stop configuration comprises a first stop element arranged at said first gear and a second stop element arranged at said second gear, said first stop element and said second stop element being arranged to bias against each other in said mounting. and wherein said first and second stop elements are arranged to be separated from each other in said engaging position. Through said stop elements, said mounting position is effectively facilitated, and because they are separated from each other in the engaging position, the scissor function functions without any of the stop elements having to be removed.
    According to an embodiment of the gear configuration, said predetermined angle of rotation in the mounting position is greater than the angle of rotation in the engaging position, the angle of rotation in the engaging position being arranged to be able to vary without said first and second stop elements acting against each other.
    As a result, the scissor function of the gear configuration operates in the engaged position during operation without the stop elements touching each other and thus impairing the function.
    According to an embodiment of the gear configuration, said spring load is arranged to be provided by means of an annular spring means with a main extension plane substantially perpendicular to the axial direction of the gear configuration, said spring means being arranged in a groove with a main extension plane substantially angularly. This enables compact and efficient biasing.
    According to an embodiment of the gear configuration, said first stop element comprises a stop lug arranged in said groove, and said second stop element comprises a stop pin inserting in said groove arranged to act against said stop lug in said mounting position.
    In this way an efficient and compact stop function is obtained in the mounting position utilizing the groove intended for the spring member. According to an embodiment of the gear configuration, said stop pin is arranged to be applied at an angle of rotation which at least amounts to said predetermined angle of rotation in the mounting position. This enables an efficient locking in the mounting position with a predetermined torque, ie. predetermined bias voltage.
    According to an embodiment of the gear configuration, said stop pin is constituted by a screw element. This facilitates the achievement of the mounting position in that the stop pin can be screwed in when sufficient pretension is present so that the stop pin can be inserted into the groove so that it can act against the stop lug. Furthermore, removal of the stop pin is made possible, which facilitates, for example, replacement of spring means.
    According to an embodiment of the gear configuration, said first gear comprises at least one recess comprising a first shallow portion running in the circumferential direction of the gear and a second deeper portion adjacent to an end of said shallow portion, and said second gear comprising at least one pin with said pin. at least one recess. This makes it easier to have fixed pins when biased to said mounting position. Furthermore, stable and simple control and fitting of said at least one pin is made possible for obtaining said mounting position.
    According to an embodiment of the gear configuration, said first stop element comprises a circumferential portion of said second deeper portion of said at least one recess, and said second stop element comprises a portion of said at least one pin. This enables efficient locking in the mounting position in said deeper portion of the recess.
    According to an embodiment of the gear configuration, said first and second stop elements are arranged to cooperate in a first stage in such a way that said at least one pin is inserted into said shallow portion of said at least one recess in connection with the end opposite said deeper portion 10. of said shallower portion, and so that said at least one pin is inserted into said deep portion by mutual rotation and subsequent axial displacement of said gears, whereby said mounting position is achieved.
    According to an embodiment of the gear configuration, said at least one pin in said engaging position is displaceable in circumferential direction in said deep portion without acting against the periphery of said deep portion. As a result, the scissor function of the gear configuration operates in the engaging position during operation without said at least one pin touching the periphery of the deep portion and thus deteriorating the function.
    According to an embodiment of the gear configuration, said pin forms an integral part of said second gear. This prevents the pin from coming loose / screwing up in an axial direction away from the first gear and coming loose from the entire gear configuration and ending up outside the gear configuration and risk affecting other units of a vehicle such as the engine / drive unit. Because it is integrated in the second gear and faces the first gear, in the event that a pin should come off, the pin will not end up outside the gear configuration without being retained in it and thus not cause damage to units outside the gear configuration_ According to an embodiment of the gear configuration pin removably disposed at said second gear. This makes it possible, in gear configurations where possible, to remove the pin when it is in the engaging position, so as to avoid any influence of said pin during operation. DESCRIPTION OF THE DRAWINGS The invention is described with reference to the following exemplary description which refers to the accompanying drawings, in which like reference numerals refer to like parts throughout the several views, and in which: Fig. 1a schematically shows a side view of a motor vehicle; Fig. 1b schematically shows a perspective view of a brake compressor in a part of a transmission configuration according to the present invention; Fig. 2a schematically shows a perspective view of a scissor-type gear configuration according to a first embodiment of the present invention; Fig. 2b schematically shows an exploded perspective view of the gear configuration of Fig. 2a; Fig. 3a schematically shows a plan view of the gear configuration of Fig. 2a in a mounting position; Fig. 3b schematically shows a plan view of a detail of the gear configuration in Fig. 3a; Fig. 3c schematically shows a cross section A-A of the gear configuration in Fig. 3a; Fig. 4a schematically shows a perspective view of parts of the gear configuration in Fig. 2a; Fig. 4b schematically shows a perspective view of a gear of the gear configuration in fig. 2a; Fig. 5a schematically shows a perspective view of a gear configuration according to a second embodiment of the present invention; Fig. 5b schematically shows an exploded perspective view of the gear configuration of Fig. 5a; Fig. 5c schematically shows a perspective view of a gear of the gear configuration of fig. 5a; Fig. 6a schematically shows a plan view of the gear configuration of Fig. 5a in a mounting position; Fig. 6b schematically shows a cross section A-A of the gear configuration in Fig. 6a; Fig. 7a schematically shows a perspective view of parts of the gear configuration in fi g.5a, and Fig. 7b schematically shows a perspective view of details of a gear configuration according to a variant of the second embodiment before mounting.
    DESCRIPTION OF EMBODIMENTS Referring to Figure 1a, a schematic vehicle 1 is shown. The exemplary vehicle 1 consists of a heavy vehicle in the form of a truck. The vehicle can alternatively be a bus or a car. The vehicle comprises an engine comprising a scissor type gear configuration according to the present invention.
    Fig. 1b schematically shows a perspective view of a brake compressor 2 of an engine in a part of a transmission configuration 3 in the form of an engine transmission according to the present invention. The transmission configuration 3 comprises a scissor type gear configuration I in the form of a brake compressor gear configuration. Said gear configuration I is arranged to cooperate in an engaging position together with a further gear 5 in the form of a camshaft gear in the transmission configuration. During operation, the scissor function of the gear configuration causes noise reduction due to the gear engagement between the gear configuration and the additional gear. The operation and construction of the scissor-type gear configuration of the present invention are described below in embodiments.
    Fig. 2a schematically shows a perspective view of a scissor type gear I according to a first embodiment of the present invention, Fig. 2b an exploded perspective view of the gear configuration I in Fig. 2a, Fig. 3a a plan view of the gear configuration I in fig. Fig. 2a in a mounting position, Fig. 3b a detail I 'of the gear configuration I in Fig. 3a, and Fig. 3c a cross-section A-A of the gear configuration I in Fig. 3a. Furthermore, Fig. 4a schematically shows a perspective view of parts of the gear configuration I in Fig. 2a and Fig. 4b shows a perspective view of a gear 30 of the gear configuration in Fig. 2a.
    The gear configuration I here corresponds to the gear configuration in fig. 1b.
    The gear configuration I comprises a first gear 10 and a second gear 30 arranged coaxially with and rotatably relative to said first gear 10. The first gear 10 has a set of teeth 10a and the second gear 30 has a corresponding number of teeth 30a so that when the first and second gear the gear 30 are coaxially arranged relative to each other, the teeth 10a of the first gear 10 and the teeth 30a of the second gear 30 can be aligned.
    Said first gear 10 comprises a hub portion 12 and a tooth portion 14 concentrically arranged relative to the hub portion 12, the hub portion 12 projecting from the tooth portion 14 with a first portion 12a projecting from the second gear 30 and a second portion 12b projecting towards the second gear 30.
    The first gear 10 has a coaxially continuous opening 15 running through the hub portion 12 with a circular cross-section for connection to a shaft of a device, for example a brake compressor according to Fig. 1b. Said second gear 30 has an axially continuous through opening 31 arranged to enclose said second projecting portion 12b of the first gear 10, an end portion of the second projecting portion 12b being arranged to project from it from the first gear. 10 from the opposite side of the second gear 30.
    The gear configuration I further comprises a retaining means in the form of a tracking ring element 40 arranged around said end portion of the second projecting portion 12b to prevent axle | relative movement between the first and second gears 30. As can be seen from Fig. 2a, among other things, the tracking ring element 40 is consequently arranged to axially lock the first gear 10 at the second gear 30, while the first and second gears 10, 30 are rotatably arranged relative to each other.
    Said first gear 10 comprises, as can be seen, inter alia, from Fig. 2b, a groove 16 with a main extension plane substantially perpendicular to the axial direction of the first gear 10 and consequently of the gear configuration.
    Said groove 16 is arranged in the gear portion 14 of the first gear 10 and is facing the side of said second gear 30 which is intended to be brought coaxially against said first gear 10. Said groove 16 has a substantially circular extent. Said groove 16 extends between said teeth 10a and said hub portion 12 in the circumferential direction of the first gear 10.
    The gear configuration I comprises a first stop element 18 arranged in the groove 16 of the first gear 10, which according to this embodiment comprises an elevation or stop lug 19 in the groove 16 with a first side 19a and a relatively said first side 19a extending substantially perpendicular to the direction of extension of the groove 16. substantially opposite second side 19b. Through said first stop element 18, said annular groove 16 is given a horseshoe shape (C-shape). The gear configuration I comprises an annular spring member 50 in the form of a torsion spring member with a main extension plane substantially perpendicular to the axial direction of the gear configuration I. Said spring means 50 has a horseshoe configuration, said spring means having a first end portion 50a and a second end portion 50b. Said spring means 50 is arranged in said groove 16 of the first gear 10. Said groove 16 is consequently arranged to house said spring means 50 as shown in Fig. 4a.
    Said first end portion 50a of the spring member 50 is arranged to abut against the first side 19a of the stop lug 19 of the first stop element 18.
    As shown in Fig. 5c, the gear configuration I comprises a biasing element 32 projecting axially from the second gear 30.
    The biasing element 32 is arranged to abut in the groove 16 against the other end 50b of the spring member 50. The biasing element 32 is consequently arranged in the groove 16 arranged between the stop lug 19 and the second end portion 50b of the spring member 50.
    Said gear configuration I is arranged to be spring-loaded by means of said annular spring means 50 so that a bias of the gear configuration I is obtained. Said spring load is arranged to be provided by mutually rotating said first and second gears 10, 30 so that said biasing element acts against the second end portion 50b of the spring member 50.
    Said gear configuration I comprises a second stop element arranged at the second gear 30 comprising a stop pin 35 intended to be inserted into the groove 16 of the first gear 10. According to a variant, the stop pin 35 is intended to be inserted through a through opening 32a arranged in the second gear 30 in connection to and at a distance from the biasing element 32. Said gear configuration I is arranged to be biased in a pre-assembly position by mutually rotating said first and second gears 10, 30 so that said stop pin 35 can be attached to the second gear 30. so that it projects axially and is inserted in said groove 16 between the stop lug 19 of the first stop element 18 of the first gear 10 and the biasing element 32 of the second gear 30. The stop pin 35 is according to an embodiment of a screw element which is arranged to be screwed in connection to said pre-assembly position.
    Accordingly, said stop pin 35 is arranged to be fitted in said pre-mounting position, said first and second gears 10, 30 being arranged to be mutually rotated with a torque corresponding to an angle of rotation relative to each other to the pre-mounting position so that the stop pin 35 is allowed to be axially configured. the groove 16 between the stop lug 19 and the second end portion of the spring member 50.
    The angle of rotation shown in Fig. 3b is for illustrative purposes only and is therefore exaggerated to clarify the function. The angle depends, among other things, on the dimension of each gear. The displacement between a gear of the first gear and a gear of the second gear is in the mounting position according to a variant of the order of <1 mm, and depends, among other things, on the dimension of the respective gears and the preload.
    The stop pin 35 is arranged to be arranged so that it is at a distance from the biasing element 32. The stop pin 35 is consequently in the pre-assembly position intended to be fixedly arranged at the second gear 30 so that the biasing element 32 and the stop pin 35 fixedly arranged at the second gear 30 can rotate with the second gear 30.
    Said first and second gears 10, 30 are arranged to in a mounting position shown in Figs. 3a-c mutually spring-loaded rotatably assume a position where said first and second gears 10, 30 deviate from each other from said engaging position. In said mounting position, said stop pin 35 is arranged to act against said stop lug 19. Because the stop pin 35 is arranged between the stop lug 19 and the second portion 50b of the spring member 50, the spring-loaded spring member 50 will by spring force act against the biasing element 32, the second gear 30 will be rotated by spring force until the stop pin 35 stops against the other side 19b of the stop lug 19. Fig. 4a shows the gear configuration I without the second gear 30 showing how the stop pin 35 acts against the stop lug 19.
    Said first and second gears 10, 30 of the gear configuration I are arranged to cooperate in an engaging position together with a further gear in a transmission configuration, for example an engine transmission.
    An example of this is shown in Fig. 1b. Fig. 2a shows the engaging position of the gear configuration I, where said additional gears are not shown.
    Said first and second gears 10, 30 are arranged to be mutually rotatably arranged against a spring force in the engaging position with said further gears. Said first and second gears 10, 30 are arranged to be mutually spring-loaded with a predetermined torque in the engaged position.
    Said first and second gears 10, 30 are as shown in Fig. 3b in said mounting position arranged to deviate by a predetermined angle of rotation v from said engaging position. The mounting position corresponds to a predetermined biasing spring load where said first and second gears 10, 30 are prevented from being positioned. corresponding to a biasing spring load less than said predetermined biasing spring load. Said stop pin 35 is in this case arranged to act against the stop lug 19 so that said predetermined prestressing spring load is not undershot.
    Said first stop element 18 comprising said stop lug 19 and said second stop element comprising said stop pin 35 constitute a stop configuration arranged to prevent the assumption of a position corresponding to a biasing spring load less than said predetermined biasing spring load.
    Said deviation with a predetermined angle of rotation corresponds to a deviation between the respective gear 10a of the first gear 10 and the respective gear 30a of the second gear 30 of the gear configuration I so that said further gears are allowed to engage the gear in which the gear and the respective teeth of the second gear 30 are aligned with each other, the spring load increasing.
    Said first and second gears 10, 30 are in said engaging position arranged to assume a position where said biasing spring load is greater than the predetermined biasing spring load predetermined in said mounting position, the deviation being smaller than in the mounting position.
    Said stop lug 19 of the first stop element 18 and said stop pin 35 of the second stop element are arranged to be separated from each other in said engaging position.
    Accordingly, said stop pin 35 is separated from the stop lug 19 in the engaging position, the distance between the stop pin 35 and the stop lug 19 being such that during operation in the engaging position when said further gears are engaged with the gear configuration I and said further gears and gears relative to each other in gear configuration the distance of the stop pin 35 to the stop lug 19 is varied, the stop pin 35 does not touch the stop lug 19. Consequently, a play is formed in which the stop pin 35 is arranged to move relatively and at a distance from the stop lug 19 within said play. The stop pin 35 is further arranged in the groove 16 at a distance from the groove walls and the groove bottom.
    Accordingly, said predetermined angle of rotation v in the mounting position is larger than the angle of rotation in the engaging position, the angle of rotation in the engaging position being arranged to be able to vary without the stop pin 35 and the stop lug 19 acting against each other.
    By using the stop lug 19 in the groove 16 and a stop pin 35 as above, an efficient and compact stop function in the mounting position is obtained by using the groove intended for the spring member 50. This facilitates the achievement of the mounting position in that the stop pin 35 can be screwed in when sufficient preload is present so that the stop pin 35 can be inserted into the groove 16 so that it can act against the stop lug 19. Furthermore, removal of the stop pin 35 is made possible which facilitates replacement of spring means 50.
    Fig. 5a schematically shows a perspective view of a gear configuration 11 according to a second embodiment of the present invention, Fig. 5b an exploded perspective view of the gear configuration 11 in Fig. 5a, Fig. 5c a perspective view of a gear 70 of the gear configuration in Fig. 5a, 6a is a plan view of the gear configuration of FIG. 5a in a mounting position, and Fig. 6b a cross-section A-A of the gear configuration 11 in Fig. 6a.
    The gear configuration 11 according to the second embodiment comprises in accordance with the first embodiment a first gear 60 and a second gear 70 arranged coaxially with and rotatably relative to said first gear 60. The gear configuration 11 according to the second embodiment further comprises in accordance with a first embodiment said first gear 60 according to this embodiment comprises in accordance with the first embodiment a groove 66 with a main extension plane substantially perpendicular to the axial direction of the gear configuration 11, the gear configuration 11 axial direction arranged to be housed in a groove 66 with the corresponding main extension plane. Said spring load is also in this embodiment arranged to be provided by mutually rotating said first and second gears 60, 70 so that a biasing element 73, which is shown in Fig. 5c, of the second gear 70 acts against a second end portion 80b of the spring member.
    The gear configuration 11 according to the second embodiment differs mainly by the design of the stop configuration.
    Said first gear 60 of the gear configuration 11 according to the second embodiment has an annular peripheral region 61 with a main extension plane substantially perpendicular to the axial direction of the first gear 60. Accordingly, said peripheral area 61 extends circumferentially around said annular grooves 66 and has a radial extension from the outer edge of the groove 66 to the teeth 60a of the first gear 60.
    Said first gear 60 of the gear configuration 11 according to the second embodiment comprises recesses 62 arranged in said peripheral region 61. According to this embodiment, the first gear 60 has three spaced apart and substantially symmetrically distributed recesses 61.
    Each recess 62 has an elongate shape forming an elongate groove arranged to run circumferentially along said peripheral region 61 of the first gear 60. Each recess 62 comprises a first elongated shallow portion 62a extending in the circumferential portion of the first gear 60 and a second deep groove portion 62. adjacent one end of said shallow portion 62a.
    Said deeper portion 62b has a substantially circular cross-section. Said deeper portion 62b has a first side at the end of the shallower portion 62a constituting a first circumferential portion 63a and an opposite second side constituting a second circumferential portion 63b.
    The second gear 70 of the gear configuration 11 according to the second embodiment comprises pins 72 arranged so that they can be inserted into the recesses of the first gear 60. According to this embodiment, the second gear 70 consequently has three pieces spaced apart from each other and substantially symmetrically around it. the first gear 60 facing the surface 10 15 20 25 17 distributed pins 72. Said pins 72 are arranged to cooperate with said recesses 62, i.e. a respective pin 72 is arranged to cooperate with a respective recess 62. Said recesses 62 are dimensioned to receive said pins 72.
    The gear configuration 11 comprises a first stop element 62b, 63a arranged in the respective recess 62 of the first gear 60. Said first stop element comprises said first circumferential portion 63a of said second deeper portion 62a of respective recess 62.
    Said gear configuration 11 comprises a second stop element arranged at the second gear 70 comprising said pins 72 intended to be inserted into said recesses 62 of the first gear 60. A portion of the respective pin 72 constitutes a respective second stop element.
    Said respective recess 62 and said respective pin 72 are arranged to cooperate in a first stage in such a way that respective pin 72 is inserted into the corresponding respective shallow portion 62a of respective recess 62 in connection with the end of said shallower portion opposite said deeper portion 62b. 62a, and so that the respective pin 72 is inserted into said deep portion 62b by mutual rotation and subsequent axial displacement of said gears 60, 70. As a result, a prestressed spring-loaded mounting position is obtained in accordance with the mounting position according to the first embodiment.
    Said first and second gears 60, 70 are consequently arranged to in a mounting position shown in Figs. 6a-b rotatably assume a mutually spring-loaded position where said first and second gears 60, 70 deviate from each other from said engaging position. In said mounting position, the respective pin 72 is arranged to act against the corresponding respective first circumferential portion 63a of the deeper portion 62b of the respective recess 62.
    Said first and second gears 60, 70 of the gear configuration 11 are in accordance with the first embodiment arranged to cooperate in an engagement position together with a further gear in a transmission configuration, for example a high-pressure pump. Fig. 5a shows the engaging position of the gear configuration 11, where said additional gears are not shown.
    Said first and second gears 60, 70 are arranged to be mutually rotatably arranged against a spring force in the engaging position with said further gears. Said first and second gears 60, 70 are arranged to be spring-loaded with a predetermined torque in the engaged position.
    Said first and second gears 60, 70 are in accordance with the first embodiment in said mounting position arranged to deviate by a predetermined angle of rotation from said engaging position. The mounting position corresponds to a predetermined prestressing spring load where said first and second gears 60, 70 are prevented from occupying a position corresponding to a prestressing spring load less than said predetermined prestressing spring load, the respective pin 72 being arranged to act against respective deeper first holes 62 said predetermined biasing spring load is not undershot.
    Said first stop element comprising respective first circumferential portion 63a and said second stop element comprising respective pin 72 constitute a stop configuration arranged to prevent intake of a position corresponding to a biasing spring load less than said predetermined biasing spring load.
    Said deviation with a predetermined angle of rotation corresponds to a deviation between the respective gear 60a of the first gear 60 and the respective gear 70a of the second gear 70 of the gear configuration 11 so that said further gears are allowed to engage the respective gear gear 10. The first gear 60 and the respective gear 70a of the second gear 70 are aligned with each other, whereby the spring load increases.
    Said first and second gears 60, 70 are in said engaging position arranged to assume a position where said prestressing spring load is greater than the predetermined prestressing spring load predetermined in said mounting position, the deviation being smaller than in the mounting position.
    Said first circumferential portion of the respective recess 62 of the first stop element and the respective pin 72 of the second stop element are arranged to be separated from each other in said engaging position.
    Accordingly, the respective pin 72 is separated in the engaging position from the first circumferential portion 62b of the respective recess 62 deeper portion 62a and the second circumferential portion 63b, the distance between the respective pin 72 and the circumferential portions 63a, 63b of the recess portion being such that during operation in the engaging position said further gear in engagement with the gear configuration 11 and said further gears and the gear configuration 11 are rotated relative to each other so that the distance of the pin to the circumferential portions 63a, 63b is varied, the pin 72 does not touch the circumferential portions 63a, 63b. Accordingly, a clearance is formed in which the respective pin 72 is arranged to move relative and at a distance from the first and second circumferential portions 63a, 63b of the deeper portion of the respective recess 62 within said clearance.
    The respective pins are arranged at a distance from the bottom of the respective deeper pañi62b.
    Consequently, said predetermined angle of rotation in the mounting position is greater than the angle of rotation in the engaging position, the angle of rotation in the engaging position being arranged to be able to vary without the respective pin 72 and the first circumferential portion 63a of the deeper portion 62 of each recess 62 acting against each other. The respective pin 72 in said engaging position is displaceable in circumferential direction in said deep portion 62b without acting against the periphery of the respective deep portion 62b, i.e. first and second circumferential portions 63a, 63b. According to the second embodiment, respective pins form an integral part of said second gear 70. Because the respective pin 72 is integrated, the pin 72 comes loose and ends up outside the gear configuration and risks affecting other units of a vehicle such as engine / drive unit. .
    Fig. 5c does not show the pins but only openings 72a intended for the pins 72. The pins can be integrated by being permanently attached to the openings.
    According to an alternative variant shown in Fig. 7b, the pins can be removably arranged at said openings, the openings according to the variant in Fig. 7b being continuous so that the pins can be removed in an axial direction away from the first gear.
    The recesses according to the second embodiment for inserting pins for locking in mounting position facilitate to have integrated pins when prestressed to said mounting position. Furthermore, with the recesses with shallow portion and deep portion, stable and simple control and adjustment / presetting of said at least one pin is made possible for obtaining said mounting position.
    Fig. 7b schematically shows a perspective view of parts of a gear configuration 11 'according to a variant of the second embodiment before mounting.
    The gear configuration differs from the second embodiment only in that the respective pin 72 'is removably arranged at the second gear 70'. This makes it possible, in gear configurations where possible, to remove the pin when it is in the engaging position, so as to avoid said pin breaking during operation and causing problems.
    In connection with the second embodiment and the variant of the said recesses, including first stop elements and said pins including second stop elements, the above have consisted of three symmetrically arranged recesses with a corresponding number of pins intended to be inserted into the recesses. Alternatively, the gear configuration has one recess, two recesses or more than three recesses corresponding to the recesses described above, with one pin, two pins or several pins.
    The above description of the preferred embodiments of the present invention has been provided for illustrative and descriptive purposes. It is not intended to be exhaustive or to limit the invention to the variations described. Obviously, many modifications and variations will occur to those skilled in the art. The embodiments have been selected and described to best explain the principles of the invention and its practical applications, thereby enabling one skilled in the art to understand the invention for various embodiments and with the various modifications appropriate to the intended use.
    Thus, for example, the described engine can be used in other applications for vehicles, for example engines for industrial or marine use. Likewise, it is not necessary that the invention be used for engines but can be used generally in transmissions where scissor-type gears are included. The figures shown for the description example have shown gears with oblique teeth, but these can have another shape such as straight teeth.
    权利要求:
    Claims (18)
    [1]
    A scissor-type gear configuration (l; ll; ll ') comprising a first gear (10; 60) and a second gear (30; 70) arranged coaxially with and rotatably relative to said first gear (10; 60), said gear being arranged to co-operate with a further gear (5) in a transmission configuration, said first and second gears being arranged to be mutually rotatably arranged against a spring force in an engaged position with said further gears, characterized in that said first and second gears are arranged to in a mounting position mutually spring-loaded rotatably assume a position where said first and second gears (10; 60, 30; 70) deviate from each other from said engaging position.
    [2]
    Gear configuration according to claim 1, wherein said first and second gears (10; 60, 30; 70) in said mounting position are arranged to deviate by a predetermined angle of rotation (v) from said engaging position and this position corresponds to a predetermined biasing spring load where said first and second gears (10; 60, 30; 70) are prevented from occupying a position corresponding to a biasing spring load less than said predetermined biasing spring load.
    [3]
    A gear configuration according to claim 2, comprising a stop configuration (18, 19, 35; 62b, 63a, 72; 72 ') arranged to prevent ingestion of a position corresponding to a biasing spring load less than said predetermined biasing spring load.
    [4]
    A gear configuration according to claim 2 or 3, wherein said first and second gears (10; 60, 30; 70) in said engaging position are arranged to assume a position where said biasing spring load is greater than said predetermined biasing spring load and where the deviation is less than in mounting mode. 10 15 20 25 23
    [5]
    The gear configuration of claim 4, wherein said stop configuration (18, 19, 35; 62b, 63a, 72; 72 ') comprises a first stop member (18, 19; 62b, 63a) disposed at said first gear (10; 60) and a second stop element (35; 72; 72 ') arranged at said second gear (30; 70), said first stop element and said second stop element being arranged to act biased against each other in said mounting position, and wherein said first and second stop elements are arranged to be separated from each other in said engaging position.
    [6]
    Gear configuration according to claim 5, wherein said predetermined angle of rotation (v) in the mounting position is greater than the angle of rotation in the engaging position, wherein the angle of rotation in the engaging position is arranged to be able to vary without said first and second stop elements acting against each other.
    [7]
    A gear configuration according to any one of claims 1-6, wherein said spring load is arranged to be provided by means of an annular spring means (50; 80) with a main extension plane substantially perpendicular to the axial direction of the gear configuration, said spring means (50; 80) being arranged in a groove (16; 66) having a major plane of extension substantially perpendicular to the axial direction of the gear configuration (l; ll; ll ').
    [8]
    A gear configuration according to any one of claims 7, wherein said first stop member comprises a stop lug (19) arranged in said groove (16; 66), and said second stop member comprises a stop pin (35) inserted in said groove (16; 66) arranged to in said mounting position act against said stop lug (19).
    [9]
    Gear configuration according to claim 8, wherein said stop pin (35) is arranged to be applied at an angle of rotation which at least amounts to said predetermined angle of rotation (v) in the mounting position.
    [10]
    A gear configuration according to claim 8 or 9, wherein said stop pin (35) is constituted by a screw element. 10 15 20 25 24
    [11]
    A gear configuration according to any one of claims 5-7, wherein said first gear (60) comprises at least one recess (62) comprising a first shallow portion (62a) extending in the circumferential direction of the gear and a second deeper portion (62b) adjacent an end of the gear said shallow portion (62a), and wherein said second gear (70) comprises at least one pin (72; 72 ') arranged to cooperate with said at least one recess (62).
    [12]
    The gear configuration of claim 11, wherein said first stop member comprises a circumferential portion (63a) of said second deeper portion (62b) of said at least one recess (62), and said second stop member comprises a portion of said at least one pin (72) .
    [13]
    The gear configuration of claim 12, wherein said first and second stop members are arranged to cooperate in a first stage such that said at least one pin (72) is inserted into said shallow portion (62a) of said at least one recess (62) in connection to the end of said shallower portion (62a) opposite to said deeper portion (62b), and so that said at least one pin (72) by mutual rotation and subsequent axial displacement of said gear is inserted into said deep portion (62b), whereby said mounting position is reached.
    [14]
    A gear configuration according to claim 13, wherein said at least one pin (72) in said engaging position is circumferentially displaceable in said deep portion (62b) without acting against the periphery of said deep portion.
    [15]
    A gear configuration according to any one of claims 12-14, wherein said pin (72) forms an integral part of said second gear (70).
    [16]
    A gear configuration according to any one of claims 12-14, wherein said pin (72) is removably disposed at said second gear (70).
    [17]
    Transmission configuration comprising a gear configuration (l; ll; ll ') according to any one of claims 1-16.
    [18]
    An engine comprising a transmission configuration according to claim 17.
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    同族专利:
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    SE535289C2|2012-06-19|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1051012A|SE535289C2|2010-09-30|2010-09-30|Sax type gearwheel configuration|SE1051012A| SE535289C2|2010-09-30|2010-09-30|Sax type gearwheel configuration|
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