CN116447072A - Cycloid motor and braking method thereof - Google Patents
Cycloid motor and braking method thereof Download PDFInfo
- Publication number
- CN116447072A CN116447072A CN202310584740.3A CN202310584740A CN116447072A CN 116447072 A CN116447072 A CN 116447072A CN 202310584740 A CN202310584740 A CN 202310584740A CN 116447072 A CN116447072 A CN 116447072A
- Authority
- CN
- China
- Prior art keywords
- motor
- piston
- brake
- output shaft
- assembly
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000000034 method Methods 0.000 title claims abstract description 12
- 229910000831 Steel Inorganic materials 0.000 claims description 11
- 239000010959 steel Substances 0.000 claims description 11
- 230000006835 compression Effects 0.000 claims description 8
- 238000007906 compression Methods 0.000 claims description 8
- 238000004891 communication Methods 0.000 claims description 4
- 238000001125 extrusion Methods 0.000 claims description 4
- 230000007423 decrease Effects 0.000 claims description 3
- 238000006073 displacement reaction Methods 0.000 claims 1
- 230000002035 prolonged effect Effects 0.000 abstract description 4
- 239000003921 oil Substances 0.000 description 42
- 230000009471 action Effects 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 230000003111 delayed effect Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C4/00—Oscillating-piston engines
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/64—Electric machine technologies in electromobility
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Hydraulic Motors (AREA)
Abstract
The invention discloses a cycloid motor and a braking method thereof, wherein the cycloid motor comprises: the motor assembly and the brake shell are connected with one end of the brake shell; the output shaft is connected with the other end of the brake shell, and one end of the output shaft is positioned in the brake shell; the linkage shaft is positioned in the output shaft, one end of the linkage shaft is connected with the motor assembly, and the other end of the linkage shaft is connected with the output shaft; the brake assembly is positioned in the brake shell and sleeved on the output shaft; the elastic piece is arranged in the brake shell and is positioned at one side of the brake assembly; a piston is mounted within the brake housing, with the piston being located on the other side of the brake assembly. The elastic piece and the piston are respectively arranged at two sides of the braking component, so that the wear on the piston can be obviously reduced and the service life of the cycloid motor can be prolonged while the braking function is realized.
Description
Technical Field
The invention relates to the technical field of hydraulic motors, in particular to a cycloid motor and a braking method thereof.
Background
The cycloid motor is an internal meshing cycloid gear type hydraulic motor and has the advantages of simple structure, good low-speed performance and strong short-term overload capacity. Cycloidal motors require a brake to be provided when in use. The existing cycloid motors mainly comprise two types, namely a cycloid motor without a brake and a cycloid motor with a brake, and the cycloid motor without the brake is required to be provided with an additional brake when in use, so that the whole volume is increased, and the cost is increased. The existing cycloid motor with the brake has the advantages that the whole size is reduced, but the piston and the spring are arranged on the same side of the friction pair, the spring directly presses the piston to brake the acting force of the friction pair family, and the piston always receives the acting force of the spring, so that the piston is seriously worn, and the service life of the cycloid motor is short. The piston of the cycloidal motor is required to be customized, has a complex shape and high manufacturing cost, and the cost is obviously increased when one piston is replaced. Accordingly, existing gerotor motors with their own brakes still have shortcomings and need to be improved.
Disclosure of Invention
The present invention aims to solve at least one of the technical problems existing in the prior art.
Therefore, the invention provides a cycloid motor and a braking method thereof, wherein the elastic piece and the piston are respectively arranged at two sides of the braking component, so that on one hand, the braking effect can be still realized; on the other hand, the abrasion to the piston can be obviously reduced, and the service life of the cycloid motor is prolonged.
The technical scheme adopted for solving the technical problems is as follows: a gerotor motor, comprising:
motor assembly
A brake housing having one end connected to the motor assembly;
the output shaft is connected with the other end of the brake shell, and one end of the output shaft is positioned in the brake shell;
the linkage shaft is positioned in the output shaft, one end of the linkage shaft is connected with the motor assembly, and the other end of the linkage shaft is connected with the output shaft;
the brake assembly is positioned in the brake shell and sleeved on the output shaft;
an elastic member installed in the brake housing, the elastic member being located at one side of the brake assembly;
a piston is mounted within the brake housing and the piston is located on the other side of the brake assembly.
Further, the brake assembly includes: the friction pair is sleeved on the output shaft, the outer ring of the friction pair is connected with the sleeve, and the baffle ring is located between the sleeve and the elastic piece.
Further, a first annular groove is formed in one side, close to the motor assembly, of the piston, a high-pressure cavity is formed in the motor assembly, and the first annular groove is communicated with the high-pressure cavity.
Further, the motor assembly includes: the motor shell is connected with the motor body, the motor shell is connected with the brake shell, a first side wall is arranged on one side, close to the brake shell, of the motor shell, and the piston is located between the brake shell and the first side wall.
Further, a first step surface is formed on the inner wall of the brake housing, the piston is located between the first step surface and the motor housing, the distance between the first step surface and the motor housing is L, the thickness of the piston is H, and the maximum moving distance Δl=l-H of the piston.
Further, a second side wall is arranged in the brake shell, the second side wall is opposite to the first side wall, an accommodating space is formed between the second side wall and the inner wall of the brake shell, the elastic piece is installed in the accommodating space, and the friction pair and the baffle ring are both located between the first side wall and the second side wall.
Further, a first flow passage and a second flow passage are further formed in the piston, one end of the first flow passage is communicated with the first annular groove, and the other end of the first flow passage is communicated with one end of the second flow passage; and a third flow passage is formed in the first side wall, and when the output shaft is braked, the other end of the second flow passage is communicated with the third flow passage.
Further, a throttling element is embedded in the first flow passage, the diameter of the throttling hole of the throttling element is d, and the value range of d is 0.15mm-0.4mm.
Further, a locating pin is arranged between the sleeve and the brake housing.
Further, the friction pair includes: the novel clutch comprises a plurality of steel sheets and a plurality of friction plates, wherein the outer ring of the steel sheets is connected with the sleeve, the inner ring of the friction plates is connected with the output shaft, and the steel sheets and the friction plates are arranged at intervals.
Further, the friction plate includes: friction plates with and without oil drainage grooves, wherein the ratio between friction plates with and without oil drainage grooves is 1:1.
The invention also provides a braking method of the cycloid motor, which comprises the following steps:
s1, starting a motor assembly, wherein high-pressure oil of the motor assembly enters a brake shell so as to push a piston to move leftwards;
s2, when the piston moves leftwards, the elastic piece is compressed, at the moment, the compression force applied by the brake assembly is reduced, the braking force is relieved, and the motor assembly can drive the output shaft to rotate through the linkage shaft;
and S3, when the high-pressure oil is stopped from being introduced into the brake shell, the piston starts to move rightwards, at the moment, the extrusion force born by the elastic piece is reduced, the compression force born by the brake assembly is increased, the braking force is increased, the output shaft cannot rotate, and braking is realized.
Further, when the piston moves leftwards, the sleeve is pushed to move leftwards, the sleeve pushes the baffle ring to move leftwards, the elastic piece is pressed by the baffle ring, at the moment, the distance between the baffle ring and the first side wall is increased, the friction force of the friction pair is reduced, and the braking is released.
Further, when the brake shell stops introducing high-pressure oil, the piston gradually moves rightward, so that the second flow channel is communicated with the third flow channel, the high-pressure oil in the first annular groove can be discharged through the first flow channel, the second flow channel and the third flow channel, and at the moment, the friction force of the friction pair is increased, and braking is realized.
The cycloid motor has the beneficial effects that the elastic piece and the piston are respectively arranged at the two sides of the brake assembly, so that the elastic piece can not directly act on the piston, the piston is protected, and the service life of the cycloid motor is prolonged. The high-pressure cavity of the motor body is communicated with the first annular groove of the piston, and the high-pressure oil acts on the piston to drive and brake the output shaft, so that an additional brake oil port can be omitted, and the internal structure of the cycloid motor is further simplified. Through the design to piston inner structure, can realize the delay braking of stopper, be favorable to protecting the motor. Through setting the type and the number of the friction plates, the braking torque can be increased steadily, and the braking speed can be regulated and controlled.
Drawings
The invention will be further described with reference to the drawings and examples.
Fig. 1 is a perspective view of a gerotor motor of the present invention.
Fig. 2 is a cross-sectional view of the gerotor motor of the present invention (with the piston at the far right end).
Fig. 3 is a cross-sectional view of the gerotor motor of the present invention (with the piston at the leftmost end).
Fig. 4 is a cross-sectional view of the brake housing and motor housing of the present invention.
Fig. 5 is a schematic view of a brake assembly of the present invention.
Fig. 6 is a schematic view of the installation of the locating pin of the present invention.
Fig. 7 is a schematic view of the structure of the piston of the present invention.
Fig. 8 is a schematic structural view of the throttle of the present invention.
Fig. 9 is a schematic structural view of the friction pair of the present invention.
Fig. 10 is a schematic view of a friction plate with a drain groove of the present invention.
Fig. 11 is a schematic view of a friction plate of the present invention without a drain groove.
In the figure: 1. a motor assembly; 2. a brake housing; 3. an output shaft; 4. a linkage shaft; 5. a brake assembly; 6. an elastic member; 7. a piston; 8. a positioning pin; 11. a high pressure chamber; 12. a motor housing; 13. a motor body; 21. a first step surface; 22. a second sidewall; 51. a friction pair; 52. a baffle ring; 53. a sleeve; 71. a first ring groove; 72. a first flow passage; 73. a second flow passage; 74. a throttle member; 121. a first sidewall; 1211. a third flow passage; 511. a steel sheet; 512. a friction plate; 731. a second ring groove; 741. an orifice.
Detailed Description
The invention will now be described in further detail with reference to the accompanying drawings. The drawings are simplified schematic representations which merely illustrate the basic structure of the invention and therefore show only the structures which are relevant to the invention.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present invention. Furthermore, features defining "first", "second" may include one or more such features, either explicitly or implicitly. In the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
Example 1
As shown in fig. 1 to 11, the gerotor motor of the present invention includes: the motor assembly 1, the brake casing 2, the output shaft 3, the universal driving shaft 4, the brake assembly 5, elastic piece 6 and piston 7, the one end of the brake casing 2 is connected with the motor assembly 1, the output shaft 3 is connected with the other end of the brake casing 2, one end of the output shaft 3 is located in the brake casing 2, the universal driving shaft 4 is located in the output shaft 3, one end of the universal driving shaft 4 is connected with the motor assembly 1, the other end of the universal driving shaft 4 is connected with the output shaft 3, the brake assembly 5 is located in the brake casing 2, the brake assembly 5 is sleeved on the output shaft 3, the elastic piece 6 is installed in the brake casing 2, the elastic piece 6 is located on one side of the brake assembly 5, the piston 7 is installed in the brake casing 2, and the piston 7 is located on the other side of the brake assembly 5.
The motor assembly 1 can drive the output shaft 3 to rotate through the linkage shaft 4, and the braking assembly 5, the elastic member 6 and the piston 7 cooperate with each other to brake the output shaft 3. When the right side of the piston 7 receives the acting force of high-pressure oil, the piston 7 can move leftwards so as to squeeze the elastic piece 6, and at the moment, the braking force of the brake assembly 5 is released, and the output shaft 3 can rotate; when the input of high-pressure oil is stopped, the piston 7 moves rightward to realize the reset, and at this time, the brake assembly 5 can brake the output shaft 3. According to the cycloid motor, through improvement of the structure of the cycloid motor, the elastic piece 6 and the piston 7 are respectively arranged on two sides of the brake assembly 5, the elastic piece 6 does not directly act on the piston 7, abrasion to the piston 7 can be reduced, the service life of the cycloid motor is prolonged, and cost is saved.
The brake assembly 5 includes: the friction pair 51, the baffle ring 52 and the sleeve 53, the friction pair 51 is sleeved on the output shaft 3, the outer ring of the friction pair 51 is connected with the sleeve 53, and the baffle ring 52 is positioned between the sleeve 53 and the elastic piece 6. That is, the right side of the sleeve 53 contacts the piston 7, the left side of the sleeve 53 contacts the stopper ring 52, and the elastic force of the elastic member 6 can bring the stopper ring 52 into contact with the left side of the sleeve 53. The piston 7 is provided with a first annular groove 71 near one side of the motor assembly 1, the motor assembly 1 is internally provided with a high-pressure cavity 11, and the first annular groove 71 is communicated with the high-pressure cavity 11. When high-pressure oil is introduced into the high-pressure chamber 11 of the motor assembly 1, the high-pressure oil can reach the first annular groove 71 through the flow passage, the piston 7 starts to move leftwards under the action of the high-pressure oil, the sleeve 53 and the baffle ring 52 also move leftwards under the pushing of the piston 7, at this time, the extrusion force applied to the elastic member 6 is increased, the compression force applied to the friction pair 51 is reduced, the friction force is reduced, and the output shaft 3 can rotate under the driving of the motor assembly 1. When the high-pressure cavity 11 stops supplying high-pressure oil, the acting force applied to the piston 7 is reduced, the piston 7 starts to move rightwards, the friction pair 51 is compressed again under the action of the elastic piece 6, the friction force is increased, and the output shaft 3 stops rotating, so that braking is realized. According to the invention, the elastic piece 6 and the piston 7 are arranged at the left side and the right side of the friction pair 51, the elastic piece 6 acts on the baffle ring 52, so that the cost for replacing the baffle ring 52 is very low even if the baffle ring 52 is worn after long-time use, and the baffle ring 52 is a standard piece, is easy to process, is easy to acquire, and is very convenient and quick to maintain or replace. For example, a positioning pin 8 is provided between the sleeve 53 and the brake housing 2. The locating pin 8 prevents the sleeve 53 from rotating relative to the brake housing 2.
The motor assembly 1 includes: the motor housing 12 is connected with the motor body 13, the motor housing 12 is connected with the brake housing 2, a first side wall 121 is arranged on one side, close to the brake housing 2, of the motor housing 12, and the piston 7 is located between the brake housing 2 and the first side wall 121. One end of the linkage shaft 4 is connected with the motor body 13 through the motor housing 12, whereby the motor body 13 can drive the linkage shaft 4 to rotate, thereby driving the output shaft 3 to rotate. The motor housing 12 is screwed to the brake housing 2. A receiving space can be formed between the first side wall 121 and the inner wall of the brake housing 2, in which receiving space the piston 7 is located.
The inner wall of the brake housing 2 has a first step surface 21, the piston 7 is located between the first step surface 21 and the motor housing 12, the distance between the first step surface 21 and the motor housing 12 is L, the thickness of the piston 7 is H, and the maximum movement distance Δl=l-H of the piston 7. The second side wall 22 is arranged in the brake housing 2, the second side wall 22 is opposite to the first side wall 121, an accommodating space is formed between the second side wall 22 and the inner wall of the brake housing 2, the elastic piece 6 is arranged in the accommodating space, and the friction pair 51 and the baffle ring 52 are both positioned between the first side wall 121 and the second side wall 22. In other words, the first step surface 21 may limit the movement stroke of the piston 7, and the distance Δl by which the piston 7 moves leftward is equal to the compression amount of the elastic member 6 by the retainer ring 52. Let the distance between the second side wall 22 and the first side wall 121 be Y, the thickness of the friction pair 51 be H1, the thickness of the retainer ring 52 be H2, when the piston 7 is located at the rightmost end, the retainer ring 52 just presses the friction pair 51 against the first side wall 121, the friction pair 51 generates braking force, when the piston 7 is located at the leftmost end, the distance between the retainer ring 52 and the first side wall 121 increases, the pressing force applied to the friction pair 51 decreases, and the braking force is released. That is, the distance Y should be designed as Y > h1+h2+Δl, but the distance Y should not be designed to be too large in consideration of the size of the gerotor motor as a whole. For example, Δl=2 mm, y=46 mm, h1=37.5 mm, h2=6 mm. In other words, the first side wall 121 can provide a pressing action on the friction pair 51 in addition to the function of facilitating the installation of the piston 7, so that not only can the internal structure of the gerotor motor be simplified, but also the cost can be saved, and the compactness of the gerotor motor can be improved.
When the motor body 13 is started, the high-pressure oil in the high-pressure chamber 11 may flow to the first annular groove 71, but when the motor body 13 stops working, the high-pressure oil in the first annular groove 71 cannot return to the high-pressure chamber 11. However, if the high-pressure oil in the first ring groove 71 cannot be discharged, the piston 7 cannot return to the initial position (i.e., the rightmost end). In addition, when the cycloid motor is braked, the motor body 13 and the output shaft 3 are stopped, and the time required for stopping the rotation of the output shaft 3 from the supply of the high-pressure oil into the motor body 13 without friction side effects is t 2 If at time t 2 Within this, the brake assembly 5 has braked the linkage shaft 4, which may cause damage to the motor body 13 (i.e., in a state in which the motor body 13 has not been completely stopped,the brake assembly 5 forcibly brakes the linkage shaft 4). Therefore, in design, the braking time t of the output shaft 3 by the braking assembly 5 should be ensured 1 ≥t 2 . To meet the braking time t 1 ≥t 2 The present invention improves the structure of the piston 7.
Specifically, the interior of the piston 7 is also provided with a first flow channel 72 and a second flow channel 73, one end of the first flow channel 72 is communicated with the first annular groove 71, and the other end of the first flow channel 72 is communicated with one end of the second flow channel 73; the first side wall 121 is provided with a third flow passage 1211, and the other end of the second flow passage 73 communicates with the third flow passage 1211 when the output shaft 3 is braked. The first flow passage 72 is embedded with a throttle 74, the diameter of a throttle hole 741 of the throttle 74 is d, and the value of d is 0.15mm-0.4mm. In other words, when the introduction of the high-pressure oil into the first ring groove 71 is stopped, the piston 7 can move rightward by a small distance by the elastic member 6, and at this time, the other end of the second flow passage 73 can be connected to the third flow passage 1211, and the high-pressure oil in the first ring groove 71 can flow into the third flow passage 1211 through the first flow passage 72 and the second flow passage 73 and be discharged. When the piston 7 is located at the leftmost end, the volume of the cavity formed between the first ring groove 71 and the motor housing 12 is V1, and when the piston 7 is located at the rightmost end, the volume of the cavity formed between the first ring groove 71 and the motor housing 12 is V2, that is, the change of the volume of the cavity during braking of the piston 7 is Δv=v1-V2. From this, it can be found that the magnitude of Δv is related to the distance Δl, and that the larger Δl is, the larger Δv is. It will be appreciated that the time of change in DeltaV is related to the time of release of high pressure oil. The invention adjusts the release time of high-pressure oil by embedding the throttling element 74 in the first flow passage 72, thereby ensuring that the braking time meets t 1 ≥t 2 . The orifice 741 is provided in the middle of the throttle member 74, and the smaller the diameter of the orifice 741 is, the longer the liquid discharging time is, the larger the diameter of the orifice 741 is, and the shorter the liquid discharging time is, therefore, the aperture of the orifice 741 needs to be specially designed to ensure the braking time t 1 ≥t 2 。
For example, the other end of the second flow path 73 further has a second annular groove 731, a width w of the second annular groove 731 is larger than a diameter of the second flow path 73, and a width w of the second annular groove 731 is larger than a diameter of the third flow path 1211. The distance between the left side wall of the second ring groove 731 and the left end face of the piston 7 is a, the vertical distance between the left end face of the third flow channel 1211 and the first step face 21 is b, for example, a=Δl, and the width w=2×Δl, and b > a+w, so that when the piston 7 is located at the leftmost end, the second flow channel 73 is not in communication with the third flow channel 1211, and when the piston 7 moves rightward by a certain distance (for example, 5 mm), the second ring groove 731 is in communication with the third flow channel 1211, and the high-pressure oil can be discharged. According to the invention, through the design of the internal structure of the piston 7, the braking and delay braking of the output shaft 3 can be realized. According to the invention, the high-pressure oil of the motor body 13 acts on the piston 7, so that an additional brake oil port can be omitted, an additional control switch is not required for realizing a braking function, and the braking function is closed or opened according to the on/off state of the high-pressure oil in the motor body 13.
For example, the friction pair 51 includes: the outer ring of the steel sheet 511 is connected with the sleeve 53, the inner ring of the friction sheet 512 is connected with the output shaft 3, and the steel sheet 511 and the friction sheet 512 are arranged at intervals. Friction plate 512 includes: friction plates with oil drainage grooves and friction plates without oil drainage grooves. When the cycloid motor is braked, hydraulic oil can be rapidly discharged through the friction plate with the oil discharge groove, the friction force between the friction plate 512 and the steel sheet 511 is increased, the oil discharge of the friction plate without the oil discharge groove is slower, the friction force is increased slower, and when the hydraulic oil is completely discharged, the friction force between the two friction plates and the steel sheet 511 is the same. The invention can ensure that the braking torque is steadily increased through the matched use of the two types of friction plates. And the braking speed can be regulated and controlled by adjusting the proportion of the two types of friction plates. For example, the ratio between a friction plate with an oil drain groove and a friction plate without an oil drain groove is 1:1.
Example 2
The invention also provides a braking method of the cycloid motor, which comprises the following steps: s1, starting the motor assembly 1, and enabling high-pressure oil of the motor assembly 1 to enter the brake housing 2 so as to push the piston 7 to move leftwards. S2, when the piston 7 moves leftwards, the elastic piece 6 is compressed, at the moment, the compression force applied to the brake assembly 5 is reduced, the braking force is relieved, and the motor assembly 1 can drive the output shaft 3 to rotate through the linkage shaft 4. And S3, when the high-pressure oil stops flowing into the brake shell 2, the piston 7 starts to move rightwards, at the moment, the extrusion force applied by the elastic piece 6 is reduced, the compression force applied by the brake assembly 5 is increased, the braking force is increased, the output shaft 3 cannot rotate, and braking is realized.
When the piston 7 moves leftward, the sleeve 53 is pushed to move leftward, the sleeve 53 pushes the stopper ring 52 to move leftward, the elastic member 6 is pressed by the stopper ring 52, at this time, the distance between the stopper ring 52 and the first side wall 121 increases, the friction force of the friction pair 51 decreases, and the braking is released.
When the brake housing 2 stops supplying high pressure oil, the piston 7 gradually moves rightward, so that the second flow channel 73 communicates with the third flow channel 1211, and the high pressure oil in the first ring groove 71 can be discharged through the first flow channel 72, the second flow channel 73 and the third flow channel 1211, and at this time, the friction force of the friction pair 51 increases, and braking is achieved.
Compared with the prior art, the cycloid motor and the braking method thereof have at least the following advantages:
(1) By arranging the elastic piece 6 and the piston 7 on the two sides of the friction pair 51 respectively, the elastic piece 6 can not directly act on the piston 7, which is beneficial to protecting the piston 7, thereby prolonging the service life of the cycloid motor.
(2) The high pressure chamber 11 of the motor body 13 is communicated with the first annular groove 71 of the piston 7, and the high pressure oil acts on the piston 7 to drive and brake the output shaft 3, so that an additional brake oil port can be omitted, and the internal structure of the cycloid motor is further simplified.
(3) By designing the internal structure of the piston 7, on one hand, the delayed braking of the brake (the braking action time is later than the stopping time of the motor body 13) can be realized, which is beneficial to protecting the motor; on the other hand, when the motor stops supplying high-pressure oil, the high-pressure oil in the first annular groove 71 can be discharged through the flow passage, preventing the high-pressure oil from being compressed in the first annular groove 71 to cause leakage.
(4) Through setting the type and the number of the friction plates, the braking torque can be increased steadily, and the braking speed can be regulated and controlled.
With the above-described preferred embodiments according to the present invention as an illustration, the above-described descriptions can be used by persons skilled in the relevant art to make various changes and modifications without departing from the scope of the technical idea of the present invention. The technical scope of the present invention is not limited to the description, but must be determined as the scope of the claims.
Claims (14)
1. A gerotor motor, comprising:
motor assembly (1)
A brake housing (2), one end of the brake housing (2) being connected to the motor assembly (1);
the output shaft (3) is connected with the other end of the brake shell (2), and one end of the output shaft (3) is positioned in the brake shell (2);
the universal driving shaft (4) is positioned in the output shaft (3), one end of the universal driving shaft (4) is connected with the motor assembly (1), and the other end of the universal driving shaft (4) is connected with the output shaft (3);
the brake assembly (5) is positioned in the brake shell (2), and the brake assembly (5) is sleeved on the output shaft (3);
an elastic member (6), the elastic member (6) is installed in the brake housing (2), and the elastic member (6) is located at one side of the brake assembly (5);
-a piston (7), the piston (7) being mounted within the brake housing (2), and the piston (7) being located on the other side of the brake assembly (5).
2. The gerotor motor of claim 1, characterized in that the brake assembly (5) comprises: the friction pair (51), the baffle ring (52) and the sleeve (53), the friction pair (51) is sleeved on the output shaft (3), the outer ring of the friction pair (51) is connected with the sleeve (53), and the baffle ring (52) is located between the sleeve (53) and the elastic piece (6).
3. The gerotor motor of claim 2, characterized in that the piston (7) is provided with a first ring groove (71) on the side close to the motor assembly (1), the motor assembly (1) having a high pressure chamber (11) therein, the first ring groove (71) being in communication with the high pressure chamber (11).
4. A gerotor motor according to claim 3, characterized in that the motor assembly (1) comprises: the motor housing (12) is connected with the motor body (13), the motor housing (12) is connected with the brake housing (2), a first side wall (121) is arranged on one side, close to the brake housing (2), of the motor housing (12), and the piston (7) is located between the brake housing (2) and the first side wall (121).
5. The gerotor motor of claim 4, characterized in that the brake housing (2) has a first step surface (21) on its inner wall, the piston (7) being located between the first step surface (21) and the motor housing (12), the distance between the first step surface (21) and the motor housing (12) being L, the thickness of the piston (7) being h, the maximum displacement distance Δl = L-h of the piston (7).
6. The cycloidal motor according to claim 4, characterized in that a second side wall (22) is provided in the brake housing (2), the second side wall (22) being disposed opposite to the first side wall (121), a receiving space being formed between the second side wall (22) and the inner wall of the brake housing (2), the elastic member (6) being mounted in the receiving space, and the friction pair (51) and the retainer ring (52) being disposed between the first side wall (121) and the second side wall (22).
7. The cycloidal motor according to claim 4, characterized in that a first flow channel (72) and a second flow channel (73) are further formed in the piston (7), one end of the first flow channel (72) is communicated with the first ring groove (71), and the other end of the first flow channel (72) is communicated with one end of the second flow channel (73); the first side wall (121) is provided with a third flow passage (1211), and when the output shaft (3) is braked, the other end of the second flow passage (73) is communicated with the third flow passage (1211).
8. The gerotor motor of claim 7, characterized in that the first flow channel (72) is embedded with a throttle (74), the diameter of the throttle (741) of the throttle (74) is d, and d is in the range of 0.15mm-0.4mm.
9. Cycloidal motor according to claim 2, characterized in that a locating pin (8) is arranged between the sleeve (53) and the brake housing (2).
10. The gerotor motor of claim 2, characterized in that the friction pair (51) comprises: the novel clutch comprises a plurality of steel sheets (511) and a plurality of friction plates (512), wherein the outer ring of the steel sheets (511) is connected with a sleeve (53), the inner ring of the friction plates (512) is connected with an output shaft (3), and the steel sheets (511) and the friction plates (512) are arranged at intervals.
11. The gerotor motor of claim 10, wherein the friction plate (512) includes: friction plates with and without oil drainage grooves, wherein the ratio between friction plates with and without oil drainage grooves is 1:1.
12. A method of braking a gerotor motor of any one of claims 1 to 11, characterized by the steps of:
s1, starting a motor assembly (1), and enabling high-pressure oil of the motor assembly (1) to enter a brake shell (2) so as to push a piston (7) to move leftwards;
s2, when the piston (7) moves leftwards, the elastic piece (6) is compressed, at the moment, the compression force applied by the brake assembly (5) is reduced, the braking force is relieved, and the motor assembly (1) can drive the output shaft (3) to rotate through the linkage shaft (4);
s3, when high-pressure oil is stopped from being introduced into the brake shell (2), the piston (7) starts to move rightwards, at the moment, the extrusion force born by the elastic piece (6) is reduced, the compression force born by the brake assembly (5) is increased, the braking force is increased, and the output shaft (3) cannot rotate, so that braking is realized.
13. Braking method according to claim 12, characterized in that when the piston (7) moves to the left, the sleeve (53) is pushed to the left, the sleeve (53) pushes the stop ring (52) to the left, the elastic member (6) is pressed by the stop ring (52), at this time, the distance between the stop ring (52) and the first side wall (121) increases, the friction force of the friction pair (51) decreases, and the braking is released.
14. The braking method according to claim 12, wherein when the brake housing (2) stops supplying the high pressure oil, the piston (7) gradually moves rightward, so that the second flow passage (73) communicates with the third flow passage (1211), the high pressure oil in the first ring groove (71) can be discharged through the first flow passage (72), the second flow passage (73), and the third flow passage (1211), and at this time, the friction force of the friction pair (51) increases, thereby realizing braking.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310584740.3A CN116447072A (en) | 2023-05-22 | 2023-05-22 | Cycloid motor and braking method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310584740.3A CN116447072A (en) | 2023-05-22 | 2023-05-22 | Cycloid motor and braking method thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116447072A true CN116447072A (en) | 2023-07-18 |
Family
ID=87133956
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310584740.3A Pending CN116447072A (en) | 2023-05-22 | 2023-05-22 | Cycloid motor and braking method thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116447072A (en) |
-
2023
- 2023-05-22 CN CN202310584740.3A patent/CN116447072A/en active Pending
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR101505231B1 (en) | Hydraulic coupling assembly | |
| WO2012169159A1 (en) | Relief valve | |
| KR20080073233A (en) | Two stage check valve for automatic transmission system | |
| CN216142768U (en) | Electro-hydraulic control proportional reversing valve | |
| JP2012522297A (en) | Pressure regulating valve, especially for automatic transmissions in vehicles | |
| CN116447072A (en) | Cycloid motor and braking method thereof | |
| US7717690B2 (en) | Gear pump | |
| CN214424646U (en) | Axial plunger pump | |
| CN112253558B (en) | Load control valve integrating large-flow overflow function into main valve core | |
| JP2544075Y2 (en) | pressure switch | |
| EP0513871A2 (en) | Variable displacement swash-plate type compressor | |
| JP3386052B2 (en) | Pump device | |
| CN111005851B (en) | Displacement feedback variable mechanism of hydraulic plunger pump and hydraulic plunger pump | |
| CN112302895A (en) | Axial plunger pump | |
| EP3559493B1 (en) | Wet clutch assembly | |
| JP2006097895A (en) | Self bleeding device | |
| JP3836673B2 (en) | Variable displacement pump | |
| KR960029655A (en) | Hydraulic power transmission coupler | |
| WO1997033110A1 (en) | Safety valve | |
| EP4085199A1 (en) | Reversible gerotor pump system | |
| CN102808867B (en) | Plunger clutch and vehicle provided with plunger clutch | |
| CN220353989U (en) | Radial plunger motor | |
| US20070161452A1 (en) | Limited slip differential with friction using a pressure generating device | |
| CN217354981U (en) | Valve bush valve core assembly, power valve, hydraulic power mechanism and engineering machinery | |
| CN220319723U (en) | Hydraulic motor with novel braking system and engineering vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |