CN114263585B - Piston pump - Google Patents
Piston pump Download PDFInfo
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- CN114263585B CN114263585B CN202111546755.8A CN202111546755A CN114263585B CN 114263585 B CN114263585 B CN 114263585B CN 202111546755 A CN202111546755 A CN 202111546755A CN 114263585 B CN114263585 B CN 114263585B
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- 230000005540 biological transmission Effects 0.000 claims abstract description 66
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 46
- 239000010959 steel Substances 0.000 claims abstract description 46
- 238000003754 machining Methods 0.000 claims description 7
- 238000009434 installation Methods 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 3
- 238000005096 rolling process Methods 0.000 abstract description 7
- 230000010349 pulsation Effects 0.000 abstract description 6
- 230000033001 locomotion Effects 0.000 description 9
- 230000008878 coupling Effects 0.000 description 7
- 238000010168 coupling process Methods 0.000 description 7
- 238000005859 coupling reaction Methods 0.000 description 7
- 239000012530 fluid Substances 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000004323 axial length Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 238000003756 stirring Methods 0.000 description 4
- 241000227287 Elliottia pyroliflora Species 0.000 description 3
- 230000000712 assembly Effects 0.000 description 3
- 238000000429 assembly Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000007667 floating Methods 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000010030 laminating Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000005287 neuromuscular process controlling balance Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000006748 scratching Methods 0.000 description 1
- 230000002393 scratching effect Effects 0.000 description 1
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Abstract
The invention provides a piston pump, which comprises a pump shell and a pump core, wherein the pump shell comprises a first end cover, a pump shell and a second end cover which are sequentially and coaxially arranged along an axis, the first end cover, the pump shell and the second end cover are fixedly connected to form a pump shell structure, and a steel sleeve is nested in the pump shell in an interference mode. The first pump core and the second pump core are coaxially arranged in the pump shell along the axis, have the same structure, are arranged on the transmission through shaft according to a certain phase angle and are connected with the transmission through shaft and the ball bearings for transmission. The invention greatly improves the pulsation and vibration of the pump through the through-shaft transmission double-pump structure, adopts the through-shaft rolling torque transmission structure in a transmission mode, greatly reduces the volume and weight of the pump, and independently transmits the transmission through shaft and the first and second pump cores respectively.
Description
Technical Field
The invention relates to a piston pump, and belongs to the technical field of fluid machinery.
Background
A pump is an energy conversion device that converts mechanical energy into fluid pressure energy, and is typically used to output high pressure fluid. In the conventional pumps such as a common piston type pump, a vane type pump, a gear type pump and a screw type pump, the kinematic pair of the mechanical structure of the pump is mainly in a sliding friction mode in the working process, so that a large amount of friction energy loss is generated, the shape of parts is complex, and the processing cost is high.
The piston pump with double degrees of freedom of motion integrally designs a shaft and a piston, realizes continuous oil suction and discharge by utilizing the principle of motion with double degrees of freedom of circumferential rotation and axial reciprocation of the piston, and omits a valve plate structure of the traditional plunger pump. Meanwhile, a symmetric cam roller structure is adopted to replace a slipper swashplate structure, the original sliding friction pair is changed into rolling friction, and the symmetric stress structure ensures that the piston is not stressed in the radial direction, so that two friction pairs of the piston, a cylinder body and a valve plate are omitted, the pump efficiency is higher, and the restriction of the sliding friction pair on the pump performance and the like is broken through.
In the existing dual freedom of movement piston pump structure, there are mainly the following problems: 1. the cam roller adopts the fixed support structure to support, because the existence of machining precision and assembly clearance, the roller on the fixed support can not all contact with the cam, and the atress on the piston is not the complete symmetry in theory like this, and the atress of unbalanced load is born by the bush on piston and the cylinder body, and such result must cause the plunger to form a pair of sliding friction pair with the bush on the cylinder body, reduces the efficiency of pump, takes place the adhesion jamming of piston in the cylinder body simultaneously easily. 2. The shifting fork coupling structure adopted when the double pumps are connected in series enables the pump body structure to be longer, the upper coupling shifting and lower coupling mode enables the characteristics of the two pump cores to be coupled together, high speed is not facilitated, meanwhile, the structure mode and assembly clearance of the shifting fork and the coupling cannot accurately guarantee the phase difference of the upper coupling pump core and the lower coupling pump core, and therefore the instantaneous flow value of the double pump output is not a constant value, and larger flow pulsation still exists. 3. The cam disc has a large structural form and size, and the resistance loss of the cam disc in fluid is large when the cam disc works at high speed. 4. The adopted cylinder body has complex structure, heavy weight, long process route and high time and economic cost.
Patent CN201720439347.5 discloses a tandem two-dimensional piston oil transfer pump, which adopts an intermediate coupling mode to connect double pumps, the cross section, volume and weight of the pump are very large, the hydraulic power of the pump rotation is also lost greatly, meanwhile, the transmission structure is complex, the tandem double pump structure needs to transfer torque for multiple times, and the structure is unstable and is easy to be damaged under the condition of high speed and heavy load; patent 201610779346.5 discloses a two-dimentional duplex plunger pump of floating, and this structure is connected into an organic wholely with the piston through the roller axle, and the round pin axle is done circumference along the piston on the gyro wheel and is rotated, and guide rail (cam dish) can be followed plunger axial under the effect of plunger intracavity fluid simultaneously to realize laminating all the time of gyro wheel and guide rail (cam dish). However, the roller and the piston are connected into a whole, the offset load force on the roller is finally borne by the piston and the bushing on the cylinder body, and meanwhile, the floating structure of the guide rail (cam disc) ensures that the inertial force on the piston and the roller always reverses the axial component force of the supporting force of the guide rail (cam disc) acting on the roller, so that the friction loss of the roller and the cam disc is increased.
The existing two-dimensional piston pump is complex in structure, high in processing difficulty, and poor in reliability of the pump structure, and the rollers cannot be guaranteed to be always in contact with the curved surface of the guide rail in the high-speed operation process, so that the pump is high in vibration and impact.
Disclosure of Invention
The invention aims to overcome one of the defects in the prior art and provides a piston pump.
The technical solution of the invention is as follows: the piston pump comprises a pump shell and a pump core, wherein the pump shell comprises a first end cover, a pump shell and a second end cover which are sequentially and coaxially arranged along an axis, the first end cover, the pump shell and the second end cover are fixedly connected to form a pump shell structure, a steel sleeve is embedded in the pump shell in an interference fit manner, the first pump core and the second pump core are coaxially arranged along the axis in the pump shell, the first pump core and the second pump core are consistent in structure and are arranged on a transmission through shaft according to a certain phase angle, and the transmission through shaft and a ball are connected for transmission;
the first pump core and the second pump core comprise plungers, guide rails, mounting seats and rollers, one ends of the plungers are fixedly connected with the guide rails to form a guide rail plunger assembly, the other ends of the plungers are provided with distribution grooves, the distribution grooves are arranged in steel sleeves, and the steel sleeves are correspondingly provided with distribution groove processing oil ports and are communicated with a pump shell inner flow passage; the mount pad fixed mounting is in the terminal surface of pump case, and the gyro wheel is installed on the mount pad, cooperates with the guide rail.
Compared with the prior art, the invention has the beneficial effects that:
(1) The invention greatly improves the pulsation and vibration of the pump through the through-shaft transmission double-pump structure, adopts the through-shaft rolling torque transmission structure in a transmission mode, greatly reduces the volume and weight of the pump, and independently transmits the transmission through shaft and the first and second pump cores respectively;
(2) According to the invention, the plunger and the double-sided guide rail are integrated, the rotary reciprocating motion resistance of the guide rail plunger assembly is reduced, the oil stirring power loss of the guide rail in rotary reciprocation is greatly reduced, the efficiency of the pump is improved, and the guide rail and roller structures are intensively distributed on one side, so that the axial length of a pump core is reduced, and the volume and weight of the pump are reduced;
(3) The invention adopts the embedded integrated steel sleeve structure of the pump shell, saves the processing period and the cost of the pump, ensures the coaxiality of the first pump core and the second pump core, and improves the working reliability of the pump;
(4) The invention has simple structure, convenient processing, high working reliability and high mechanical efficiency;
(5) The invention adopts the balance supporting structure, avoids the faults of overload damage of the roller, adhesion clamping stagnation between the plunger and the bush and the like caused by the inclination of the plunger and the scratching of the copper bush due to the stress of the unilateral roller, thereby improving the long-time working reliability and mechanical efficiency of the pump and being beneficial to realizing the high-speed rotation speed of the product;
(6) The invention adopts a clearance compensation structure to effectively compensate the clearance caused by machining precision, assembly clearance and abrasion, so that the rollers on the balancing frames on the upper side and the lower side of the cam are always attached to the cam surface, the impact vibration of the pump is reduced, the operation of the pump is more reliable, and the service life of the pump is prolonged;
(7) The invention adopts a hollow double-sided guide rail structure, the rotary reciprocating motion resistance of the guide rail plunger assembly is reduced, the oil stirring power loss of the guide rail rotary reciprocating is greatly reduced, the efficiency of the pump is improved, the guide rail roller structure is intensively distributed on one side, the axial length of the pump core is reduced, and the volume and the weight of the pump are reduced.
Drawings
FIG. 1 is a schematic diagram of the overall structure of the present invention;
FIG. 2 is a schematic view of the pump housing structure of the present invention;
FIG. 3 is a schematic view of the steel jacket structure of the present invention;
FIG. 4 is a schematic view of the structure of a guide rail plunger according to the present invention;
FIG. 5 is a schematic diagram of a first pumping core rail plunger configuration of the present invention;
FIG. 6 is a schematic diagram showing the phase difference between the first and second pump cores according to the present invention;
FIG. 7 is a schematic view of a transmission through shaft according to the present invention;
FIG. 8 is a schematic diagram of a balanced support structure according to the present invention;
FIG. 9 is a cross-sectional view of FIG. 8;
FIG. 10 is a schematic view of a balance frame structure according to the present invention;
FIG. 11 is a schematic view (front view) of a mounting base according to the present invention;
FIG. 12 is a schematic view (back side) of a mounting base according to the present invention;
FIG. 13 is a schematic view of a bushing A according to the present invention;
fig. 14 is a schematic view of the bushing B according to the present invention.
Detailed Description
The invention provides a piston pump, which comprises a pump shell and a pump core, wherein the pump shell comprises a first end cover, a pump shell and a second end cover which are sequentially and coaxially arranged along an axis, the first end cover, the pump shell and the second end cover are fixedly connected to form a pump shell structure, and a steel sleeve is nested in the pump shell in an interference mode. The first pump core and the second pump core are coaxially arranged in the pump shell along the axis, have the same structure, are arranged on the transmission through shaft according to a certain phase angle and are connected with the transmission through shaft and the ball bearings for transmission.
The first pump core and the second pump core comprise plungers, guide rails, mounting seats and rollers, one ends of the plungers are fixedly connected with the guide rails to form a guide rail plunger assembly, the other ends of the plungers are provided with distributing grooves, the distributing grooves are arranged in steel sleeves through bushings A and B, and the steel sleeves are provided with distributing grooves correspondingly to be provided with distributing ports and communicated with a flow passage in a pump shell; the gyro wheel is installed on the mount pad, with the guide rail centre gripping in the middle, mount pad fixed mounting is at the terminal surface of pump case.
The invention adopts the embedded integrated steel sleeve structure of the pump shell, removes the cylinder body structure with heavy weight, complex structure and complex process, can greatly lighten the weight of the piston pump and saves the processing period and the cost of the pump. Meanwhile, the inner hole of the steel sleeve can be formed by one-step machining, so that the coaxiality of the first pump core and the second pump core is ensured, the problems of eccentric wear and adhesion of the plunger caused by different coaxiality of the first pump core and the second pump core are solved, and the working reliability of the pump is improved.
The plunger and the double-sided guide rail are integrated to form the guide rail plunger assembly, and compared with the traditional plunger with two single-sided cam structures arranged on two sides, the hollow double-sided guide rail structure has the advantages that the number of guide rail discs is reduced, the guide rail discs are matched with fixed bolt type rollers, the turning radius of the guide rail discs is reduced, the rotating and reciprocating resistance of the guide rail plunger assembly is reduced, the oil stirring power loss of the guide rail rotating and reciprocating is greatly reduced, and the efficiency of the pump is improved; meanwhile, the guide rail and the roller structures are intensively distributed on one side, so that the axial length of the pump core is reduced, and the volume and the weight of the pump are reduced.
The present invention will be described in detail with reference to specific examples and drawings.
As shown in fig. 1, the piston pump comprises a pump shell and a pump core, wherein the pump shell comprises a first end cover 1, a pump shell 2 and a second end cover 4 which are sequentially and coaxially arranged along an axis, the first end cover, the pump shell 2 and the second end cover are fixedly connected through screws to form a pump shell inner cavity, and a steel sleeve 3 is nested in an inner hole of the pump shell 2 in an interference manner. The transmission through shaft 5, the first pump core 6, the ball 11 and the second pump core 9 are arranged in the inner cavity, the first pump core 6 and the second pump core 9 are arranged on the transmission through shaft 5 according to a certain phase angle, and the transmission through shaft 5 and the ball 11 are connected for transmission.
Preferably, the first pump core 6 and the second pump core 9 are installed on the transmission through shaft 5 by adopting a double-pump serial structure with phase angles of 45 degrees.
The transmission through shaft 5 is shown in fig. 1 and 7 and is in a stepped shaft form, and comprises bearing mounting sections 51 and 52 at two ends and a transmission section 53 in the middle, wherein the transmission section 53 is provided with two groups of linear ball channels 54 parallel to the axis along the axial direction and used for placing balls 11, and when the transmission through shaft 5 rotates, the transmission through shaft 5 drives the balls 11 to move so as to realize a torque transmission function. The transmission through shaft 5 is connected with the first end cover 1 and the second end cover 4 through shaft seals and fixed bearings.
The 2 groups of ball grooves 54 on the transmission through shaft 5 correspond to the ball grooves of the plunger inner holes of the first pump core and the second pump core respectively, and balls 11 are placed in the ball grooves. The transmission through shaft 5 drives the guide rail plunger assemblies of the first pump core and the second pump core to rotate through the balls, and meanwhile, the guide rail plunger assemblies axially reciprocate under the guidance of the curved surfaces of the guide rails.
Further, each group of linear ball grooves 54 are uniformly distributed in the circumferential direction of the transmission through shaft 5, and all the linear ball grooves 54 have the same length and depth.
Preferably, the ball is at a clearance Δl=h+κd in the linear ball channel, where h is the rail travel, D is the ball diameter, and κ is the clearance coefficient.
If the clearance coefficient κ is too small, much smaller than 0.1, for example smaller than 0.01, the balls may slide in the ball grooves rather than roll, and the balls Yi Ka are in the ball grooves; if the clearance coefficient κ is too large, for example, greater than 1.0, the generated tilting moment is large, and the motion between the drive shaft and the plunger may be affected, so that interference is formed between the drive shaft and the plunger. More preferably, the value of κ is in the range of 0.1 to 0.5.
Further preferably, the length of the linear ball channel 54 is l=nd+h+κd, where n is the number of balls, and the number of balls is determined according to the bearing capacity of the balls and the torque to be transmitted, and is specifically set as known in the art.
Because the linear ball channels 54 are not fully covered by the balls, and the initial positions of the balls on the channels are inconsistent, the balls can generate a tilting moment on the transmission through shaft and the plunger, and the tilting moment is balanced through the supporting bearings (fixed bearings and bushings) of the transmission through shaft and the plunger by designing the clearance values of the balls in the channels.
According to the invention, the straight groove rolling torque transmission matched with the transmission through shaft and the ball is adopted to replace the traditional shifting fork transmission structure, so that the length dimension of the shifting fork structure in the axial direction is omitted, and the overall length dimension of the pump is greatly reduced; the two ends of the transmission through shaft are limited by the bearings, and the transmission through shaft is respectively and independently transmitted with the first pump core and the second pump core, so that compared with shifting fork transmission in which the first pump core and the second pump core are coupled together, the transmission is more stable and reliable, and the speed is higher.
Further, the transmission through shaft, the linear ball channel on the transmission through shaft, the ball grooves on the plungers of the first pump core and the second pump core, the distribution groove and the molded surface of the guide rail are completed by one-time clamping. The linear ball channel on the transmission through shaft is in clearance-free fit with the linear ball channel on the plunger, and the guide rail plunger assembly can accurately ensure that the instantaneous flow output by the first pump core and the second pump core is always kept constant, so that flow pulsation and pressure pulsation are well eliminated.
Compared with the rolling torque transmission of the ball spline annular groove, the rolling torque transmission of the ball groove of the transmission through shaft is simpler and more reliable and has smaller size. However, compared with the circular rolling of the balls fully distributed in the annular grooves of the ball spline, the balls of the through shaft straight groove structure are not fully distributed in the grooves, and when initial positions of the balls on the grooves are inconsistent, the balls can generate a tilting moment on the through shaft and the plunger. The invention ensures that the tilting moment is balanced through the support bearing of the through shaft and the plunger by specially designing the clearance value of the balls in the channel.
As shown in fig. 2, two ends of the pump shell 2 are respectively processed into counter bores 28, the mounting seats 7 for respectively placing two pump cores are arranged at the centers of the counter bores 28, two groups of oil distributing ports 26 are uniformly distributed on the inner wall of the through bore 27 along the circumferential direction, the oil distributing ports 26 are aligned one by one along the axial direction, and the oil distributing ports correspond to plunger oil distributing grooves of the first pump core and the second pump core respectively. The bottom surface of the counter bore 28 is circumferentially provided with a plurality of high-pressure oil through holes 23 and low-pressure oil through holes 22, the high-pressure oil through holes 23 are respectively communicated with corresponding oil distributing holes 26 and lead to the pump outlet 21 from the middle, and the high-pressure oil through holes 23 are blocked by the mounting seat 7; the low pressure oil passage holes 22 communicate with the pump inlet and with the corresponding oil distribution holes 26.
Further, threaded holes 25 are circumferentially distributed on the bottom surface of the counter bore 28 and are used for fixedly mounting the mounting seat 7; lug grooves 24 matched with the steel sleeve 3 are processed on the circumference of the inner hole 27 and are used for installing lugs 35 of the steel sleeve 3, so that limit of the lugs 35 is realized.
As shown in fig. 1,2 and 3, the steel sleeve 3 is in a cylindrical structure, the steel sleeve 3 is nested in an inner hole 27 in the pump shell 2 in an interference manner, a supporting lug 35 is machined on the outer wall of one end and matched with a supporting lug groove 24 machined on the inner hole 27, the supporting lug groove is used for axially limiting and angularly positioning of the interference installation of the steel sleeve 3 and the pump shell 2, and after the installation, the distributing ports 32 on the steel sleeve 3 are in one-to-one correspondence with the distributing ports of the inner hole of the pump shell 2.
The first plunger 62 and the second plunger 92 are placed in the inner hole 31 of the steel sleeve 3, and the inner hole 31 is formed by one-step processing, so that the coaxiality of the first pump core 6 and the second pump core 9 can be better ensured. Two groups of oil distribution ports 32 are uniformly distributed on the steel sleeve 3 along the circumferential direction, and the oil distribution ports 32 are aligned one by one along the axial direction and respectively correspond to oil distribution grooves of the first plunger 62 and the second plunger 92.
Further, an oil through port 33 is formed between the two groups of oil distribution ports 32, so that a closed space is prevented from being formed between the first plunger and the second plunger, and oil is prevented from being trapped.
The middle part of the inner hole of the steel sleeve is provided with a middle bushing B10, pin holes 34 arranged at two ends of the oil through holes 33 correspond to semicircular pin grooves 103 on the outer wall of the middle bushing B10, and the middle bushing B10 can be fixed in the inner hole of the steel sleeve 3 through cylindrical pins; and the two ends of the inner hole of the steel sleeve are provided with bushings 8.
The first pump core and the second pump core have the same structure and comprise plungers, bushings, mounting seats, rollers and guide rails. The present invention describes the first pump core and the second pump core structure by taking the structure of the first pump core 6as an example.
The first pump core, as shown in fig. 1, 4,5, 8, includes a first mount 7, a first rail 61, a first plunger 62, a first bushing A8, an intermediate bushing B10, and a first roller 64. One end of the first plunger 62 is fixedly provided with a first guide rail 61 and is fixedly connected through a pin 63 to form a guide rail plunger assembly, the transmission through shaft drives the guide rail plunger assembly to rotate, and meanwhile, the guide rail plunger assembly axially reciprocates under the guidance of a guide rail curved surface. The other end of the first plunger is mounted in the steel sleeve inner hole 31 through the first bushing A8 and the middle bushing B10. The first mounting seat 7 is mounted in the counter bore 28 in the end face of the pump housing 2, and the first roller 64 is mounted on the first mounting seat 7 with the first rail 61 sandwiched therebetween.
The guide rail plunger assembly comprises a first guide rail 61 and a first plunger 62, which are fixedly connected by a pin 63, as shown in fig. 4 and 5. The first guide rail 61 is a double-sided guide rail, the middle is a through hole, a transmission flat 611 is arranged in the through hole, pin holes 612 are formed in the outer wall of the double-sided guide rail 61 inwards, and the distance between the two pin holes 612 is the same as the diameter of an inner hole of the double-sided guide rail.
The plunger integrates three functions of flow distribution, oil suction and discharge and transmission. One end of the first plunger 62 is provided with a transmission flat 621 and a pair of semicircular pin grooves 622; the first plunger 62 penetrates into the inner hole of the first guide rail, and the transmission flat 611/621 corresponds to the pin holes 612/622 one by one and is fixedly connected into a whole through the cylindrical pin 63; the other end is a distributing end, a plurality of oil distributing grooves 624 are circumferentially and uniformly distributed, a first bushing A8 and a middle bushing B10 are arranged at two ends of the oil distributing grooves 624, and the distributing end of the first plunger 62 is arranged in an inner hole of the steel sleeve 3 through the first bushing A8 and the middle bushing B10.
Further, four oil distribution grooves 622 are uniformly distributed on the distribution end along the circumferential direction, and are corresponding to the steel sleeve and the pump shell, and the oil inlet and the oil outlet are respectively 2 and are symmetrically distributed in pairs.
The first plunger 62 is provided with an inner hole along the axial direction, and a plurality of linear ball grooves 623 are uniformly distributed along the circumferential direction of the inner hole and correspond to the linear ball grooves 54 processed on the transmission through shaft 5.
Further preferably, in order to make the phase angles of the two pump cores differ accurately and be easy to operate during installation, the ball grooves of the two pump core plungers are staggered by a required phase angle respectively corresponding to the highest point and the lowest point of the same pump core guide rail. As shown in fig. 6, the two pump core phase angles differ by 45 °, the ball grooves of the first plunger 62 correspond to the intermediate positions of the highest point and the lowest point of the same pump core rail 61, and the ball grooves of the second plunger 92 correspond to the highest point and the lowest point of the same pump core rail 91; when the pump is installed on a transmission through shaft, the phase angle difference of the two pump cores is ensured to be 45 degrees through the channel and the ball, and the theoretical flow of the piston pump outlet is ensured to be free from pulsation.
Compared with the prior plunger two-sided guide rail structure, the guide rail structure has the advantages that the number of guide rail discs is reduced, the guide rail discs are matched with the bolt type rollers for use, the radius of gyration of the guide rail discs is reduced, the resistance of the rotary reciprocating motion of the guide rail plunger assembly is reduced, the oil stirring power loss of the rotary reciprocating motion of the guide rail is greatly reduced, and the efficiency of the pump is improved; meanwhile, the guide rail roller structures are intensively distributed on one side, so that the axial length of the pump core is reduced, and the volume and the weight of the pump are reduced.
The invention has at least 2 rollers which are uniformly distributed on the circumference of the guide rail and fixedly arranged on the mounting frame and are attached to the guide rail. Preferably, the roller adopts a bolt type roller needle bearing.
The mounting seat 7 is used for supporting the roller or the balance supporting structure, limiting the bushing and blocking the high-pressure cavity of the pump shell. The mounting seat is in a disc structure as shown in fig. 11 and 12, one end of the disc is provided with a pair of upright posts 71 in central symmetry, and the upright posts are respectively provided with a pair of pin holes 72 for mounting the roller or the balance frame; a sinking groove 76 is formed in the center of the other end of the disc, a through hole is formed in the center of the sinking groove 76, through holes 73, a plurality of oil holes 74 and a pair of cylindrical plugs 75 are symmetrically distributed in the center of the disc, the through holes 73 correspond to the threaded holes 25 on the two sides of the pump shell one by one, and the mounting seat can be fixed on the pump shell through screws; the cylinder plug 75 is provided with a sealing ring groove for sealing the high-pressure oil through hole 23 of the pump shell.
The main function of the bushing A8 is that the plunger support is sealed with the inner hole of the steel sleeve, as shown in FIG. 13, the bushing A8 is a step-shaped hollow cylinder, the inner hole 81 in the middle is used for being matched with the plunger support column, the outer wall of the boss 83 on one side is matched with the inner hole of the steel sleeve, the middle support ring 82 is used for limiting the axial direction of the steel sleeve 3, and the inner wall of the boss 84 on the other side is matched with the flow distribution end of the plunger.
The middle bushing B10 is used for supporting a plunger and is installed in the middle of an inner hole of a steel sleeve, and is of a cylindrical barrel structure, the inner hole 101 of the middle bushing is matched with a plunger flow distribution end, the outer wall of the middle bushing B10 is matched with an inner hole of the steel sleeve 3, an oil through hole 102 is formed in the side wall of the middle bushing B10 and is matched with an oil through hole 33 of the steel sleeve, and a pair of semicircular pin grooves 103 are formed in two ends of the oil through hole and are connected with the steel sleeve through pins.
Further, in order to improve the long-term operational reliability and mechanical efficiency of the pump, reduce the impact vibration of the pump, make the operation of the pump more reliable, improve the life-span of the pump, the present invention adds the balance support structure 12 between the rail-roller assemblies of the first and second pump cores, respectively.
The balance support structure, as shown in fig. 8 and 9, includes a pair of balance frames 121 for fixing the bearing forces of the rollers and the rollers on both sides of the balance rail. The balance frames are arranged on two sides of the guide rail, and the rollers are arranged on the balance frames.
As shown in fig. 10, a roller mounting hole 1212 is formed in the balance frame 121 for mounting the roller 64, an oblong pin hole 1211 is formed in the orthogonal direction of the axis of the roller 64 for connecting and positioning with the mounting seat 7, and the balance frame 121 is mounted on the mounting seat 7 by a pin 124, and the balance frame 121 can swing about the pin 124 as an axis; the simultaneous length of the circular pin holes 1211 allows the balance to be adjusted in the axial direction by a small amount, avoiding over-tightening or over-loosening of the assembly due to part machining tolerances.
In the working process, the guide rail plunger assembly is supported by a bushing A, B matched with the plunger in a rotary mode, and the reciprocating motion is supported by a roller on the balancing stand. Because of the precision of the machining, the rollers cannot be on the same horizontal plane, and if the rollers are fixed or not adjustable, the rollers cannot simultaneously contact the guide rail. And after setting up balanced bearing structure, under the regulation of balance frame, the gyro wheel that is located the guide rail with one side contacts simultaneously and even atress under the balance mechanism of balance frame, avoids appearing single gyro wheel atress and plunger slope and bush scratch, causes the inefficacy such as gyro wheel overload damage and plunger and bush adhesion jamming to improve long-time operational reliability and the mechanical efficiency of pump.
Further, as shown in fig. 8 and 9, the balance support structure is configured such that at least 2 tension springs 122 are uniformly disposed between the two balance frames 121 to convert the balance support structure and the gap compensation structure. As shown in fig. 10, a boss 1213 with a mounting hole is provided on the outside of the balance frame for mounting adjustment of the fixing screw 123 and the tension spring. As shown in fig. 8 and 9, the rollers are mounted on the balancing frames, and the balancing frames are connected through tension springs to adjust the gap between the guide rail and the rollers, so that the rollers on the balancing frames on the upper side and the lower side of the guide rail are always attached to the guide rail surface.
The invention adopts a balance supporting structure, and by arranging the structure, the supporting force of the roller to the guide rail plunger assembly is always symmetrical, and the roller overload damage caused by plunger inclination and copper bush scratch due to single-side roller stress and the failure of adhesion clamping stagnation between the plunger and the copper bush and the like are avoided, so that the long-time working reliability and mechanical efficiency of the pump are improved. Meanwhile, by arranging the tension spring structure, the gap caused by machining precision, assembly gap and abrasion can be effectively compensated, so that the rollers on the balancing frames on the upper side and the lower side of the guide rail are always attached to the guide rail surface, impact vibration of the pump is reduced, the pump is more reliable to operate, and the service life of the pump is prolonged.
The invention is not described in detail in a manner known to those skilled in the art.
Claims (13)
1. The utility model provides a piston pump, includes pump housing and pump core, and the pump housing includes first end cover, pump housing and the second end cover that sets gradually coaxial along the axis, and first end cover, pump housing and second end cover link firmly and form pump housing structure, its characterized in that: the first pump core and the second pump core are arranged in the pump shell coaxially along the axis, are consistent in structure, are arranged on the transmission through shaft according to a certain phase angle and are connected with the transmission through shaft and the ball bearings;
The first pump core and the second pump core comprise plungers, double-sided guide rails, mounting seats, balance supporting structures and rollers, one ends of the plungers are fixedly connected with the double-sided guide rails to form a guide rail plunger assembly, the other ends of the plungers are provided with distribution grooves, the distribution grooves are arranged in steel sleeves, the steel sleeves are provided with distribution ports corresponding to the distribution grooves and are communicated with a flow passage in a pump shell, the mounting seats are fixedly arranged on the end faces of the pump shell, and the rollers are arranged on the mounting seats and matched with the double-sided guide rails;
The transmission through shaft is axially provided with two groups of linear ball channels parallel to the axis, balls are arranged in the linear ball channels, the balls are not fully distributed in the linear ball channels, and the balls are in transmission fit with the first pump core and the second pump core through the linear ball channels and the balls;
The balance supporting structure comprises a pair of balance frames arranged on two sides of the double-sided guide rail, the idler wheels are arranged on the balance frames, the balance frames are arranged on the mounting seats and can rotate around the mounting points, at least 2 tension springs are uniformly arranged between the balance frames, and the axial distance between the two balance frames is adjusted under the action of the tension springs.
2. A piston pump as in claim 1, wherein: the linear ball channels are uniformly distributed on the circumference of the transmission through shaft, and the two groups of linear ball channels are consistent in axial position.
3. A piston pump as claimed in claim 2, wherein: the length of the linear ball channel is L=nD+h+kD, wherein n is the number of balls, h is the guide rail travel, D is the diameter of the balls, and k is the clearance coefficient.
4. A piston pump as claimed in claim 3, wherein: the value range of the clearance coefficient kappa is 0.1-0.5.
5. A piston pump as claimed in any one of claims 1 to 4, wherein: the two ends of the pump shell are respectively processed into counter bores for placing the mounting seats, the centers of the counter bores are through holes, two groups of oil distributing ports are uniformly distributed on the inner walls of the through holes along the circumferential direction and aligned one by one along the axial direction, and the oil distributing ports correspond to plunger distributing grooves of the first pump core and the second pump core respectively; the bottom surface of the counter bore is circumferentially provided with a plurality of high-pressure oil through holes and low-pressure oil through holes, the high-pressure oil through holes are respectively communicated with corresponding oil distributing holes, the middle part of the high-pressure oil through holes are communicated with a pump outlet, and the high-pressure oil through holes are blocked by a mounting seat; the low-pressure oil through hole is communicated with the inlet of the pump and is communicated with the corresponding oil distributing hole.
6. A piston pump as in claim 5, wherein: threaded holes are circumferentially distributed on the bottom surface of the counter bore and are used for fixedly mounting the mounting seat; and the circumference of the through hole is provided with lug grooves matched with the steel sleeve, and the lug grooves are used for installing the lug grooves of the steel sleeve, and after the installation, the distributing ports on the steel sleeve are in one-to-one correspondence with the distributing ports in the through hole of the pump shell.
7. A piston pump as claimed in any one of claims 1 to 4, wherein: the steel sleeve is of a cylindrical structure, the steel sleeve is nested in a through hole in the pump shell in an interference mode, a supporting lug is machined on the outer wall of one end of the steel sleeve, the first plunger and the second plunger are placed in an inner hole of the steel sleeve, the inner hole is formed by one-step machining, two groups of oil distributing ports are uniformly distributed on the steel sleeve along the circumferential direction, the oil distributing ports are aligned one by one along the axial direction, and the oil distributing ports correspond to oil distributing grooves of the first plunger and the second plunger respectively.
8. A piston pump as in claim 7, wherein: the two sets of oil distribution ports in the middle of offer the oil port, steel bushing hole middle part install middle bush B, through the pin hole that oil port both ends set up, correspond with the semicircular pin groove of middle bush B outer wall, steel bushing hole both ends installation bush A, the distribution end of first, two plungers is installed in the steel bushing hole through first, second bush A and middle bush B.
9. A piston pump as claimed in any one of claims 1 to 4, wherein: the double-sided guide rail is characterized in that a through hole is formed in the middle of the double-sided guide rail, a transmission flat is arranged in the through hole, two pin holes are formed in the outer wall of the double-sided guide rail inwards and are used for being fixedly connected with the plunger, and the distance between the two pin holes is the same as the diameter of the through hole of the double-sided guide rail.
10. A piston pump as claimed in any one of claims 1 to 4, wherein: one end of the plunger is provided with a transmission flat and a pair of semicircular pin grooves, the plunger is provided with an inner hole along the axial direction, and a plurality of linear ball grooves are uniformly distributed on the circumference of the inner hole and correspond to the linear ball grooves processed on the transmission through shaft.
11. A piston pump as claimed in any one of claims 1 to 4, wherein: the mounting seat is of a disc structure, a pair of upright posts are symmetrically distributed at the center of one end of the disc, pin holes for roller installation are respectively formed in the upright posts, a sinking groove is formed in the center of the other end of the disc, the center of the sinking groove is a through hole, a plurality of oil through holes and a pair of cylinder plugs are symmetrically distributed at the center of the disc, and sealing ring grooves are formed in the cylinder plugs and used for plugging the high-pressure oil through holes of the pump shell.
12. A piston pump as claimed in any one of claims 1 to 4, wherein: the transmission through shaft, the linear ball channel on the transmission through shaft, the ball channel on the plunger, the distributing groove and the molded surface of the double-sided guide rail are processed by one-time clamping.
13. A piston pump as claimed in any one of claims 1 to 4, wherein: the phase angles of the first pump core and the second pump core differ by 45 degrees, the ball grooves of one pump core plunger correspond to the middle position of the highest point and the lowest point of the same pump core guide rail, and the ball grooves of the other pump core plunger correspond to the highest point and the lowest point of the same pump core guide rail.
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| CN114941616A (en) * | 2022-04-11 | 2022-08-26 | 北京空天技术研究所 | Double-motion-freedom-degree piston single pump |
| CN116123076A (en) * | 2022-12-29 | 2023-05-16 | 北京空天技术研究所 | Piston structure and have its hydraulic piston pump |
| CN116123077B (en) * | 2022-12-29 | 2024-08-02 | 北京空天技术研究所 | Bilateral flow distribution structure and piston pump |
| CN116292262A (en) * | 2022-12-29 | 2023-06-23 | 北京空天技术研究所 | Cross torque transmission structure for piston pump and piston pump with same |
| CN116241455B (en) * | 2022-12-29 | 2024-08-02 | 北京空天技术研究所 | Piston torque transmission structure and piston pump |
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| CN106438254B (en) * | 2016-09-14 | 2018-11-06 | 李海荣 | A kind of low speed axial plunger hydraulic pump |
| CN107503901B (en) * | 2017-07-25 | 2019-03-01 | 中国民航大学 | Two-sided concave grooved cam reciprocating pump |
| CN108331890B (en) * | 2017-12-29 | 2020-07-31 | 浙江工业大学 | Spatial cam self-aligning transmission mechanism of two-dimensional plunger pump |
| CN112196760A (en) * | 2020-08-31 | 2021-01-08 | 浙江工业大学 | Novel electro-hydraulic motor |
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| CN111997856A (en) * | 2020-08-31 | 2020-11-27 | 浙江工业大学 | Two-dimensional piston pump with series-parallel structure |
| CN212898814U (en) * | 2020-09-30 | 2021-04-06 | 浙江工业大学 | Pile-up type two-dimensional piston monoblock pump |
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