CN111379839A - Cam and design method - Google Patents
Cam and design method Download PDFInfo
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- CN111379839A CN111379839A CN201811611652.3A CN201811611652A CN111379839A CN 111379839 A CN111379839 A CN 111379839A CN 201811611652 A CN201811611652 A CN 201811611652A CN 111379839 A CN111379839 A CN 111379839A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms
- F16H53/02—Single-track cams for single-revolution cycles; Camshafts with such cams
- F16H53/025—Single-track cams for single-revolution cycles; Camshafts with such cams characterised by their construction, e.g. assembling or manufacturing features
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Abstract
The invention provides a cam and a design method, which comprises a double-crest-valley cam curved surface and a middle circular boss and is characterized in that: the curved surface of the double-wave-peak wave-valley cam is smooth and continuous, and the track curve, the axial speed curve and the axial acceleration curve of the cylindrical roller wheel moving along the cam surface can be continuously guided everywhere. The cam curved surface of the invention adopts the design that the motion track curve, the axial speed curve and the axial acceleration curve of the roller are continuously guided everywhere, so that flexible impact does not exist when the pump runs, the vibration and the noise of the pump are greatly reduced, the working reliability of the pump is improved, and the problems of flexible impact and unstable working existing when the existing two-dimensional piston oil transfer pump runs are solved.
Description
Technical Field
The invention relates to a cam and a design method, in particular to a cam for a two-dimensional piston oil transfer pump and a design method, and belongs to the technical and application fields of fluid machinery.
Background
The two-dimensional piston oil transfer pump is a pump with a novel structure designed based on a two-dimensional (2D) motion principle, and a plunger of the two-dimensional piston oil transfer pump is driven by a motor to complete two-dimensional motion of circumferential rotation and axial reciprocation along two opposite cams. The speed of circumferential rotation of the rotating component is determined by the rotating speed of the motor, and the axial reciprocating characteristic is determined by the cam. Under the fixed rotating speed, the design rule of the cam curved surface directly influences the performance of the axial motion speed, acceleration, jerk and the like of the rotating part of the pump, and further influences the overall performance, vibration, noise and other characteristics of the pump. Therefore, the design rule of the cam curved surface is very important for improving the overall performance of the pump.
Patent CN207315586U discloses a serial two-dimensional piston oil transfer pump, which adopts a combination of an oblique roller and an oblique cam (fig. 1), and the curved surface of the oblique cam is designed by axial equal acceleration and deceleration rules. Although the inclined rollers can reduce sliding friction theoretically, due to the fact that the inclined rollers have radial force, the radial force of the two inclined rollers is inconsistent in the operation process of the pump, the plunger is subjected to unbalance loading, the plunger is inclined, and the plunger clamping risk is increased. Meanwhile, the cam is designed by adopting an axial equal acceleration and deceleration rule, namely, the rotating part presents equal acceleration and deceleration characteristics when moving along the cam, and the stroke, the speed and the acceleration curve are shown in figures 2a, b and c, wherein the acceleration curve is discontinuous (figure 2c), and flexible impact exists when the pump runs, so that the pump does not work stably.
Designing the trajectory curve, the axial velocity curve and the axial acceleration curve of the motion of the cam surface to be continuously guidable everywhere is a solution idea for reducing flexible impact and ensuring stable operation of the pump, but the axial acceleration curve everywhere can bring about increase of an extreme value of the axial acceleration curve, so that the inertial load of a moving part is increased, higher requirements are provided for the structural strength of the fuel pump, and finally the weight of the fuel pump can be increased.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provides a cam and a design method for improving the working reliability of an oil transfer pump and reducing the risk of plunger clamping stagnation.
The technical solution of the invention is as follows: a cam comprises a double-peak valley cam curved surface and a middle circular boss, wherein the curved surface of the double-peak valley cam curved surface is smooth and continuous, and a cylindrical roller can continuously guide along a track curve, an axial speed curve and an axial acceleration curve of the motion of a cam surface.
The curved surface shape of the double-wave-peak wave-valley cam is determined by a motion three-dimensional trajectory equation of a cylindrical roller matched with the curved surface shape, the motion three-dimensional trajectory equation of the roller is shown in a formula set (1),
x＝R cosθ
y＝R sinθ
wherein x, y and Z are strokes of the cylindrical roller in the X, Y, Z axis direction on the cam curved surface, h is the maximum stroke of the cylindrical roller along the Z axis of the cam motion, C is a constant, theta is the rotation angle of the cylindrical roller on the cam curved surface, theta ∈ [0,2 pi ], k is a sign coefficient and is an integer, when k is an even number, plus or minus in the formula (1) is taken as plus, and when k is an odd number, plus or minus in the formula (1) is taken as minus.
The constant C is determined as follows,
making the h/2 plane of the three-dimensional track of the roller motion determined by the formula group (1) and a cylinder G with the radius of R and the axis of symmetry of ZZAre coplanar with respect to the H/2 plane of (A), wherein H is a cylinder GZThe height H is more than H + phi, phi is the diameter of the roller, and R is the radius of the cam.
A knife avoiding groove with the shape similar to or the same as that of the curved surface of the cam is processed between the curved surface of the double-wave crest wave-trough cam and the middle circular boss.
A cam design method is realized by the following steps:
firstly, determining the radius R of a cam and the maximum stroke h of a roller along the Z axis of the cam;
secondly, determining a cylinder G which takes R as a radius and takes Z axis as a symmetry axisZHeight H > H + phi, phi is the diameter of the roller, and G is a cylinderZThe center of the bottom surface is a Cartesian plumbOrigin 0 of a rectilinear coordinate system XYZ;
thirdly, according to the equation of the three-dimensional track of the roller motion of the formula group (1), the constant C value is adjusted to ensure that the h/2 plane of the three-dimensional track of the roller motion and the column G determined in the second stepZCoplanar with respect to the H/2 plane of (A);
fourthly, drawing a straight line X' parallel to the X axis through the intersection point of the three-dimensional track of the roller motion and the XOZ plane, and drawing the cylinder G with the diameter phi by using the symmetrical axis of the straight line XXCylinder GXIs positioned at the same side of the YOZ plane, the height L is more than R-phi/2, and the distance between the bottom surface of the YOZ plane and the bottom surface of the YOZ plane is phi/2;
fifthly, taking the Z axis as a rotating shaft, and determining the column G in the fifth stepXPerforming volume sweep along the three-dimensional track of the roller motion and comparing with the cylinder G determined in the third stepZAnd performing Boolean subtraction to obtain a curved surface, namely the curved surface shape of the cam.
And further, a sixth step of machining the cam according to the curved surface shape of the cam determined in the fifth step and the radius R of the cam determined in the first step.
Compared with the prior art, the invention has the beneficial effects that:
(1) the cam curved surface adopts the design that the motion track curve, the axial speed curve and the axial acceleration curve of the roller are continuously guided everywhere, so that flexible impact does not exist during the operation of the pump, the vibration and the noise of the pump are greatly reduced, the reliability of the operation of the pump is improved, and the problems of flexible impact and unstable operation existing during the operation of the conventional two-dimensional piston oil transfer pump are solved;
(2) on the premise that the curve is continuously guided, the cam curved surface structure of the special roller motion three-dimensional track is determined, so that the amplitude of the axial acceleration extreme value is small, the influence on the inertial load of a motion part is small, and the influence of load increase can be met without increasing the structural strength of the original fuel pump;
(3) the curved surface of the cam is matched with the cylindrical roller, so that no radial force exists in the operation process of the pump, and the eccentric load of the plunger cannot be caused, thereby reducing the risk of plunger clamping stagnation;
(4) the design method of the invention adopts special steps to improve the accuracy of the modeling of the curved surface model, thereby ensuring the processing accuracy of the curved surface of the cam.
Drawings
FIG. 1 is a schematic structural diagram of an oblique cam and an oblique roller of a conventional two-dimensional piston oil transfer pump;
fig. 2 is a motion curve of an inclined roller of a conventional two-dimensional piston oil transfer pump, fig. 2a is a z-direction stroke curve, fig. 2b is a speed curve, and fig. 2c is an acceleration curve;
FIG. 3 is a schematic view of the cam structure of the present invention, FIG. 3a is a top perspective view, and FIG. 3b is a bottom perspective cross-sectional view;
FIG. 4 is a front view of the cam of the present invention;
FIG. 5 is a cross-sectional view taken along the line A-A in FIG. 4;
FIG. 6 is a graph of the cam motion of the present invention, with FIG. 6a being a z-stroke curve, FIG. 6b being a speed curve, and FIG. 6c being an acceleration curve;
fig. 7 is a schematic view of the cam assembly of the present invention in operation.
Detailed Description
The present invention will be described in detail with reference to the following examples and accompanying drawings.
The invention provides a cam, which comprises a double-crest-valley cam curved surface and a middle circular boss, wherein the curved surface of the double-crest-valley cam curved surface is smooth and continuous, and a cylindrical roller can continuously guide the track curve, the axial speed curve and the axial acceleration curve of the movement along the cam surface.
Further, in order to reduce the influence of continuous conduction at the axial acceleration curve on the load of the fuel pump, the following curved surface shape of the double-wave-crest and wave-trough cam is optimized.
The curved surface shape of the double wave crest wave trough cam is determined by the motion three-dimensional trajectory equation of the cylindrical roller matched with the curved surface shape, the motion three-dimensional trajectory equation of the roller is shown in a formula set (1),
x＝R cosθ
y＝R sinθ
wherein x, y, Z are the stroke of the cylinder roller in the direction of X, Y, Z axes (cartesian vertical coordinate system XYZ) on the cam curved surface, h is the maximum stroke of the cylinder roller along the Z axis of the cam motion, C is a constant, θ is the rotation angle of the cylinder roller on the cam curved surface (after rotating for one circle, the angle restarts), θ ∈ [0,2 pi ], k is a sign coefficient and is an integer, when k is an even number, ± is taken as + in the formula (1), and when k is an odd number, ± is ± taken as-, the specific value of k may be a positive or negative number according to the design requirements of the skilled person.
The constant C is determined by making the h/2 plane of the three-dimensional locus of the roller motion determined by the formula group (1) and the cylinder G having R as the radius and Z as the axis of symmetryZAre coplanar with respect to the H/2 plane of (A), wherein H is a cylinder GZThe height H is more than H + phi, phi is the diameter of the roller, and R is the radius of the cam.
A knife avoiding groove with the shape similar to or the same as that of the cam curved surface is processed between the double-wave-peak wave trough cam curved surface and the middle circular boss, and the knife avoiding groove is provided with two wave peaks and wave troughs and has the function of avoiding a grinding head when the cam curved surface is ground.
Preferably, as shown in fig. 3, 4 and 5, the cam is composed of a double-slope peak-valley cam curved surface 31 matched with the cylindrical roller and a circular boss 32, the middle of the circular boss 32 is provided with a circular matching opening 33 and a knife-avoiding groove 34 with the same shape as the cam, 4 pairs of weight-reducing oil through holes are uniformly distributed on the knife-avoiding groove 34, and the bottom surface of the cam is provided with a nut mounting counter bore 36 and a pair of process positioning holes 37.
The curved surface 31 of the double-slope peak-valley cam is determined by a motion three-dimensional trajectory equation of a cylindrical roller matched with the curved surface, and the specific result is shown in table 1.
The circular matching port 33 is positioned in the center of the circular boss 32 and is used for matching with the shaft; the nut mounting counter bore 36 and the process positioning hole 37 are positioned on the bottom surface of the cam, wherein the nut mounting hole 36 is used for accommodating a nut fastened with a shaft, and the process positioning hole 37 is used for alignment and positioning during cam processing; the shape of the blade avoiding groove 34 is similar to or the same as that of the cam curved surface, and 4 pairs of weight-reducing oil through holes are uniformly distributed in the blade avoiding groove 34 along the double axial directions.
Preferably, as shown in fig. 3b, a process positioning hole 37 is opened on the back of the slope of the cam curved surface 31 to ensure sufficient space.
Further, the invention provides a cam design method, which is realized by the following steps:
1. the cam radius R is determined.
The cam radius R is determined according to design requirements (fuel pump size, etc.), and is well known in the art, and one skilled in the art can select an appropriate size according to different structural requirements and design requirements of the fuel pump.
The cam radius R in this embodiment is 51 mm.
2. Determining the maximum Z-axis stroke h of the roller moving along the cam;
the maximum Z-axis stroke h is determined according to design requirements (fuel flow, pump speed, etc.), specifically referred to in the literature "two-dimensional (2D) piston pump principle verification research", ruian jian, lie yuan, jindingcan, butcher victory man, boy wonder, university of zhejiang academy, 2017.6.
The stroke h of the axial movement of the roller is 4 mm.
3. Determining a cylinder G with R as radius and Z axis as symmetry axisZHeight H > H + phi, phi is the diameter of the roller, and G is a cylinderZThe center of the bottom surface is the origin 0 of the cartesian vertical coordinate system XYZ.
The diameter phi of the roller is 15mm and the column G isZIs 20 mm.
4. According to the three-dimensional track equation of the roller motion determined in the table 1, the constant C value is adjusted to ensure that the h/2 plane of the three-dimensional track of the roller motion and the column G determined in the third stepZCoplanar with respect to the H/2 plane.
The constant C in this example is 10 mm.
5. Drawing a straight line X' parallel to the X axis at the intersection point of the three-dimensional track of the roller motion and the XOZ plane, and drawing a cylinder G with the diameter phi by using the symmetry axis of the straight line XXCylinder GXIs positioned at the same side of the YOZ plane, the height L is more than R-phi/2, and the distance between the bottom surface of the same and the YOZ plane is phi/2.
Column G of the present exampleXHeight L of 20mm, base distance YOZPlane 7.5 mm.
6. Taking the Z axis as a rotating axis, and taking the column G determined in the step 5XPerforming volume sweep along the three-dimensional track of the roller motion and matching the cylinder G determined in the step 3ZAnd performing Boolean subtraction to obtain a curved surface, namely the curved surface shape of the cam.
The well-known technique of volume sweep and boolean reduction operations for three-dimensional modeling of UG NX10 may be referred to by those skilled in the art.
7. And (4) processing the cam according to the curved surface shape of the cam determined in the step (7) and the radius R of the cam determined in the step (1).
When the cam is processed, a knife avoiding groove and a middle circular boss are processed between the middle circular boss and the curved surface shape of the cam. The height of the middle circular boss, the size of the central hole and other dimensions are determined according to the installation and connection relationship of the cam in the fuel pump.
Fig. 6 provides a design curve of the cam embodiment, i.e. a matching axial motion characteristic curve of the cylindrical roller, and the specific function is shown in table 1 (where the stroke h of the axial motion of the roller in this embodiment is 4). As shown in FIG. 2, the motion trail curve, the axial speed curve and the axial acceleration curve of the cam embodiment are continuously conductive everywhere, so that flexible impact does not exist when the rotating component moves along the cam, the running stability of the pump is improved, meanwhile, the extreme value of the axial acceleration is slightly increased due to the adoption of the cam curved surface defined by the motion equation in the table 2, and in the embodiment, the extreme value of the axial acceleration is 9102m/s when the pump rotates at 8000r/min2The axial inertia load of the moving part is less influenced, and the structural strength of the conventional fuel pump can meet the use requirement.
As shown in fig. 7, when the cam is mounted, the shaft 62 is inserted into the cam 61 from the circular truncated cone side and is interference-fitted with the circular fitting opening 33 of the cam 61; on the other side, a spring washer 63 is arranged in the nut mounting counterbore 36, and the plunger 62 is fastened with the cam 61 through a nut 64; the cam 61 is then mated with a pair of cylindrically fixed rollers 65.
The cam curved surface in this embodiment matches with the cylinder gyro wheel, does not have radial force in the pump operation process, can not cause the plunger unbalance loading to reduce plunger jamming risk.
The cam curved surface in the embodiment is designed by adopting a method of continuous motion track curve, continuous axial speed curve and continuous axial acceleration curve, so that flexible impact does not exist during the operation of the pump, the vibration and noise of the pump are greatly reduced, and the working reliability of the pump is higher.
TABLE 1
TABLE 2
The invention has not been described in detail and is in part known to those of skill in the art.
Claims (6)
1. The utility model provides a cam, includes the circular boss in dual crest wave trough cam curved surface and middle part, its characterized in that: the curved surface of the double-wave-peak wave-valley cam is smooth and continuous, and the track curve, the axial speed curve and the axial acceleration curve of the cylindrical roller wheel moving along the cam surface can be continuously guided everywhere.
2. A cam according to claim 1, wherein: the curved surface shape of the double-wave-peak wave-valley cam is determined by a motion three-dimensional trajectory equation of a cylindrical roller matched with the curved surface shape, the motion three-dimensional trajectory equation of the roller is shown in a formula set (1),
x＝Rcosθ θ∈[0,2π]
y＝Rsinθ θ∈[0,2π]
wherein x, y and Z are strokes of the cylindrical roller in the X, Y, Z axis direction on the cam curved surface, h is the maximum stroke of the cylindrical roller along the Z axis of the cam motion, C is a constant, theta is the rotation angle of the cylindrical roller on the cam curved surface, theta ∈ [0,2 pi ], k is a sign coefficient and is an integer, when k is an even number, plus or minus in the formula (1) is taken as plus, and when k is an odd number, plus or minus in the formula (1) is taken as minus.
3. A cam according to claim 2, wherein: the constant C is determined by making the h/2 plane of the three-dimensional track of the roller motion determined by the formula set (1) and the cylinder G with the radius of R and the axis of symmetry of ZZAre coplanar with respect to the H/2 plane of (A), wherein H is a cylinder GZThe height H is more than H + phi, phi is the diameter of the roller, and R is the radius of the cam.
4. A cam according to claim 1, wherein: a knife avoiding groove with the shape similar to or the same as that of the curved surface of the cam is processed between the curved surface of the double-wave crest wave-trough cam and the middle circular boss.
5. A cam design method is characterized by comprising the following steps:
firstly, determining the radius R of a cam and the maximum stroke h of a roller along the Z axis of the cam;
secondly, determining a cylinder G which takes R as a radius and takes Z axis as a symmetry axisZHeight H > H + phi, phi is the diameter of the roller, and G is a cylinderZThe center of the bottom surface is the origin 0 of a Cartesian vertical coordinate system XYZ;
thirdly, according to the equation of the three-dimensional track of the roller motion of the formula group (1), the constant C value is adjusted to ensure that the h/2 plane of the three-dimensional track of the roller motion and the column G determined in the second stepZAre coplanar with each other in the plane of H/2,
x＝Rcosθ θ∈[0,2π]
y＝Rsinθ θ∈[0,2π]
wherein x, y and Z are strokes of the cylindrical roller wheel in the X, Y, Z-axis direction on the cam curved surface, h is the maximum stroke of the cylindrical roller wheel along the Z-axis of the cam motion, C is a constant, theta is the rotation angle of the cylindrical roller wheel on the cam curved surface, theta ∈ [0,2 pi ], k is a sign coefficient and is an integer, when k is an even number, plus or minus in the formula (1) is taken as plus or minus, and when k is an odd number, plus or minus in the formula (1) is taken as minus;
fourthly, drawing a straight line X' parallel to the X axis through the intersection point of the three-dimensional track of the roller motion and the XOZ plane, and drawing the cylinder G with the diameter phi by using the symmetrical axis of the straight line XXCylinder GXIs positioned at the same side of the YOZ plane, the height L is more than R-phi/2, and the distance between the bottom surface of the YOZ plane and the bottom surface of the YOZ plane is phi/2;
fifthly, taking the Z axis as a rotating shaft, and determining the cylinder G in the fourth stepXPerforming volume sweep along the three-dimensional track of the roller motion and comparing with the cylinder G determined in the second stepZAnd performing Boolean subtraction to obtain a curved surface, namely the curved surface shape of the cam.
6. A method of designing a cam according to claim 5, wherein: and a sixth step of machining the cam according to the curved surface shape of the cam determined in the fifth step and the radius R of the cam determined in the first step.
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| CN201811611652.3A CN111379839A (en) | 2018-12-27 | 2018-12-27 | Cam and design method |
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| CN201811611652.3A CN111379839A (en) | 2018-12-27 | 2018-12-27 | Cam and design method |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116219643A (en) * | 2023-02-03 | 2023-06-06 | 天津工业大学 | High-speed needling robot equipment, weaving method and high-speed needling end effector |
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