CN210049997U - High-flow low-noise piston pump - Google Patents
High-flow low-noise piston pump Download PDFInfo
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- CN210049997U CN210049997U CN201920084855.5U CN201920084855U CN210049997U CN 210049997 U CN210049997 U CN 210049997U CN 201920084855 U CN201920084855 U CN 201920084855U CN 210049997 U CN210049997 U CN 210049997U
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Abstract
The utility model discloses a large-flow low-noise piston pump, the driving device of which is at least connected with a piston pump in a transmission way; the piston rod extending ends of the piston pump are connected with reciprocating guides, and cranks fixedly arranged at the output end of the driving device are hinged with the reciprocating guides through connecting rods; the rodless cavity and the rod cavity of the piston pump are respectively communicated with a one-way valve communicated with the liquid inlet and the liquid outlet, and a buffer valve seat is movably supported in a valve body of the one-way valve; one end of the valve core damping spring is supported with a buffer cushion block, and the other end of the valve core damping spring is supported on the sliding guide rod; the sealing surface of the buffer valve seat is opposite to the sealing surface of the valve core, and when the sealing surface of the buffer valve seat is attached to the sealing surface of the valve core, the gap b between the buffer valve seat and the buffer spring seat is larger than the gap a between the guide rod limiting part and the limiting top plate. The high-flow low-noise piston pump not only has higher working efficiency and realizes the high-flow delivery of the pump, but also has low operation noise and high pumping efficiency.
Description
Technical Field
The utility model relates to a fluid delivery pump especially relates to a be applied to sewage delivery pump among boats and ships bilge sewage treatment system.
Background
The harm of the bilge water of the ship has multiple aspects, and the bilge water in the bilge not only has a corrosion effect on the ship, but also can damage goods and electromechanical equipment, and seriously can also influence the normal operation of the ship; and the bilge water is collected and treated to reach the standard and then can be discharged out of the ship, otherwise, the pollution of water bodies such as oceans or rivers can be caused. Therefore, the ship bilge water treatment system is one of the most main ship systems, and the bilge water delivery pump is an indispensable important part in the bilge water treatment system.
At present, most bilge water delivery pumps adopt centrifugal delivery pumps, the centrifugal pumps have the characteristic of simple and compact structure, but the centrifugal pumps have no self-absorption capacity, and the pump body and a suction pipeline are filled with liquid before starting, so that the pump body can be filled with water only when bilge water reaches a certain depth, and the delivery pumps are started to discharge water. Obviously, the remote centralized control of sewage treatment and the continuous discharge of sewage are very inconvenient to realize, and a large amount of accumulated water at the bottom of the cabin is easy to form. Meanwhile, the centrifugal pump is not suitable for sewage conveying with small flow and large pressure head, so that the conveying efficiency is low, and the centrifugal conveying pump is difficult to be applied to a bilge water treatment system of a large ship. If the pump is not filled with water or is not full of water during the operation of the centrifugal pump, air exists in the pump shell, the centrifugal force generated after the centrifugal pump rotates is small due to the low air density, so that the low pressure formed in the central area of the impeller is not enough to suck sewage into the pump, and an 'air-bound' phenomenon is formed.
The reciprocating piston pump has the most obvious characteristics of self-absorption capacity, low sensitivity to the physical and chemical properties of sewage, capability of conveying liquid and gas mixtures, capability of achieving high pressure, no influence on the flow of the pump due to pressure change and particular suitability for bilge sewage conveying with low pulse requirements. However, the single-acting piston pump has low single-way working efficiency and large sewage output pulsation noise; the rod cavity and the rodless cavity of the double-acting piston pump are both working cavities, so that the working efficiency of the pump is improved, and the output flow of the pump is increased. However, with the upsizing of the ship, the bilge water is large in quantity, remote operation and large-flow centralized conveying treatment are required to be achieved, and the existing single-cylinder double-acting piston pump cannot meet the requirement of conveying bilge water in large flow. Especially, the check valve in the existing piston pump can generate larger beating and knocking sound in the opening and closing working process, when the check valve core is under the action of bilge water pressure, the valve core is separated from the valve seat to be opened, and when bilge water reversely flows, the fluid pressure pushes the valve core to the valve seat to be closed, so that the flow is cut off. Therefore, the valve core of the one-way valve is continuously separated from or attached to the valve seat under the action of bilge water, so that the valve core and the valve seat are frequently flapped and knocked, the reciprocating motion of the piston is accelerated along with the improvement of the working frequency of the one-way valve and the increase of pipeline pressure, and the impact between the valve core and the valve seat is more severe. The frequent and violent knocking between the valve core and the valve seat can firstly cause the damage and the breakage of the valve core or the valve seat and even cause the complete failure of the one-way valve; furthermore, frequent knocking between the valve core and the valve seat can easily cause damage to a sealing surface, so that poor sealing is caused to form reverse leakage; in addition, the working noise of the piston pump not only affects the concealment of military ships and the life and work of personnel on the ships, but also seriously affects the service performance and the service life of the pump.
SUMMERY OF THE UTILITY MODEL
The above-mentioned not enough to prior art exists, the utility model aims to solve the technical problem that a large-traffic low noise piston pump is provided, higher work efficiency not only has to realize large-traffic transport, the running noise is low moreover, realizes the calm operation.
In order to solve the technical problem, the high-flow low-noise piston pump of the utility model comprises a driving device and a piston pump in transmission connection with the driving device, wherein the driving device is in transmission connection with at least one piston pump; the piston rod extending end of each piston pump is connected with a reciprocating guide, and a crank fixedly arranged at the output end of the driving device is hinged with the reciprocating guide through a connecting rod; the cranks corresponding to the piston pumps are arranged in a staggered manner; the rodless cavity of the piston pump is respectively communicated with a one-way valve which leads to the liquid inlet and the liquid outlet, and the rod cavity of the piston pump is also respectively communicated with a one-way valve which leads to the liquid inlet and the liquid outlet; the check valve comprises a valve body, a buffer valve seat is movably supported in the valve body, a buffer spring seat is fixedly arranged on the valve body, and a buffer spring is arranged between the buffer valve seat and the buffer spring seat; a limiting top plate is fixedly supported on the valve body, the sliding guide rod is movably supported on the valve body through the limiting top plate, a guide rod limiting part is fixedly arranged at the upper end of the sliding guide rod, and the guide rod limiting part corresponds to the limiting top plate in position; a valve core is movably sleeved on the sliding guide rod, a valve core damping spring is arranged in a spring cavity of the valve core, one end of the valve core damping spring is supported with a buffer cushion block, and the other end of the valve core damping spring is supported on the sliding guide rod; the sealing surface of the buffer valve seat is opposite to the sealing surface of the valve core, and when the sealing surface of the buffer valve seat is attached to the sealing surface of the valve core, the gap b between the buffer valve seat and the buffer spring seat is larger than the gap a between the guide rod limiting part and the limiting top plate.
In the piston pump, the driving device is in parallel transmission connection with the piston pumps to form a pump structure with multiple pumps working simultaneously, so that high discharge pressure and large output flow can be generated, the working requirement of conveying sewage quickly and in large flow is met, the working efficiency of the pump is effectively improved, and the pump structure is also simplified. The piston pump piston rod extends the end and is connected with reciprocal guide, and this reciprocal guide has not only guaranteed that the piston pump piston rod is along axis direction reciprocating motion all the time, ensures the high-efficient steady work of piston pump, reduces the operation trouble of piston pump, makes the piston rod can obtain longer reciprocal stroke moreover to guarantee the increase of piston pump output flow, conveying efficiency's improvement. The driving cranks corresponding to the piston pump are arranged in a staggered mode in space, unbalance of driving loads of the driving device can be effectively reduced, and output liquid flow pulsation and pulsation noise of the output liquid flow pulsation can be effectively reduced. The rod cavity and the rodless cavity of each piston pump are respectively communicated with a one-way valve communicated with the liquid inlet and the liquid outlet, so that the multi-cylinder double-acting piston pump is formed, the rod cavity and the rodless cavity of each piston pump are working cavities, and the cranks for driving the piston rods to move are arranged in a staggered manner, so that output pulsation is further reduced, and the load of a driving device is balanced. Furthermore, because the upper end of the sliding guide rod of the one-way valve is provided with the guide rod limiting piece, when the buffer valve seat is attached to the valve core and approaches, the gap b between the buffer valve seat and the buffer spring seat is larger than the gap a between the guide rod limiting piece and the limiting top plate; when the one-way valve is closed, the pressure difference on two sides of the valve core is gradually increased, the valve core is accelerated to push to the buffer valve seat under the action of medium fluid pressure, the maximum closing speed can be reached when the valve core and the valve seat are close, the valve core drives the sliding guide rod to approach the valve seat at the moment, the valve core and the buffer valve seat collide in time, the buffer valve seat and the buffer spring firstly play a role in vibration absorption and vibration reduction and descend for a certain distance together, so that the closing speed of the valve core is; then the valve core and the sliding guide rod bring the valve seat to continue descending together, when the guide rod limiting part collides with the limiting top plate, the sliding guide rod does not move any more, because the valve core damping spring is supported on the sliding guide rod, the descending valve core starts to compress the valve core damping spring, so that the valve core damping spring and the buffer spring play a role together, the speed of the valve core is reduced, the impact of the valve core and the valve seat is reduced, the damage of a valve element and a sealing surface is avoided, and the closing noise of the valve is greatly reduced. When the check valve is opened, the medium fluid pushes the valve core to move upwards, along with the separation of valve core, disk seat, the pressure difference of valve core both sides diminishes, and the valve core up-moving speed can progressively slow down, and when the valve core was close spacing roof and during supreme utmost point was spacing, cushion block and valve core damping spring played the effect that slows down impact vibration between valve core and spacing roof jointly, reached the purpose that the damping was fallen and is fallen the noise.
In a preferred embodiment of the present invention, the driving device is in transmission connection with 2-6 piston pumps. Reasonable structure and convenient implementation.
The utility model discloses a further embodiment, drive arrangement includes the derailleur to the motor of drive derailleur. The multi-pump driving is convenient to realize.
The utility model discloses a preferred embodiment, reciprocal guide includes the guide frame, and guide frame sliding support is on the guide track, and the overhanging end of piston rod and guide frame fixed connection, the one end and the guide frame of connecting rod articulate, and the other end and the crank of connecting rod articulate, guide track and piston pump's central line parallel arrangement. The reciprocating piston rod has simple structure and can effectively ensure that the piston rod can stably reciprocate along the axis.
The utility model discloses a preferred embodiment, the space stagger angle α =80 ° -100 ° of two adjacent cranks this structure makes a piston rod have relatively less suction speed in the twinkling of an eye, and another piston rod has relatively higher suction speed in the twinkling of an eye to balanced drive arrangement load reduces output pulsation.
The utility model discloses a preferred embodiment, when the sealed face of buffering disk seat laminated with the front cover of case, the clearance b between buffering disk seat and the buffering spring holder was (2-4) times of the clearance an between guide arm locating part and the spacing roof. The speed of the valve core can be effectively reduced when the one-way valve is closed, the impact between the valve core and the valve seat is reduced, and the structure of the one-way valve is reasonable and compact.
In a further embodiment of the present invention, a guide rod lower slide seat is fixedly mounted on the buffer spring seat, the upper end of the sliding guide rod is slidably supported on the limiting top plate, and the lower end of the sliding guide rod is slidably supported on the guide rod lower slide seat; the guide rod limiting part is located above the limiting top plate. The sliding guide rod is reliable in supporting, good in sliding guidance and reliable in limiting.
In a further embodiment of the present invention, one end of the valve core damping spring is supported on the sliding guide rod through a lower support of the damping spring, and the other end of the valve core damping spring is supported by a cushion block through an upper support of the damping spring, and the cushion block is slidably sleeved on the sliding guide rod; the valve core is fixedly connected with a valve core cover plate, the buffer cushion block is movably arranged at the central position of the valve core cover plate, and the upper support of the damping spring is supported at the inner side of the valve core cover plate. The valve core can be closed and opened for vibration reduction.
In a further embodiment of the present invention, a valve seat sealing member is disposed between the buffer valve seat and the valve body; and a valve core sealing piece is arranged between the valve core and the sliding guide rod. The sealing between the moving parts is reliably realized.
In the preferred embodiment of the present invention, the valve seat sealing member and the valve core sealing member are both O-ring seals; the buffer cushion block is an elastic cushion block; the limiting top plate is fixedly supported on the valve body through a supporting rod. The sealing and vibration damping performance is stable and reliable, and the limit top plate is reliably supported.
Drawings
The present invention will be further explained with reference to the drawings and the following detailed description of the present invention.
FIG. 1 is a schematic diagram of the structure of one embodiment of the high flow, low noise piston pump of the present invention;
FIG. 2 is a schematic top view of one embodiment of the high flow, low noise piston pump of the present invention;
FIG. 3 is a main cross-sectional structural view of the embodiment of FIG. 2;
FIG. 4 is a schematic view of the cross-sectional structure A-A of FIG. 3;
FIG. 5 is a spatial position view of two cranks in the embodiment of FIG. 2;
fig. 6 is a schematic view of the structure of the check valve (in a closed state) in the embodiment shown in fig. 2.
In the figure, 1-link; 2-a crank; 3-a transmission; 4, a motor; 5-reciprocating guide, 501-guide track, 502-guide roller, 503-guide frame, 504-coupling; 6-liquid inlet; 7-a liquid outlet; 8-one-way valve, 801-sliding guide rod, 802-guide rod lower sliding seat, 803-buffer spring seat, 804-valve body, 805-supporting rod, 806-limiting top plate, 807-valve core damping spring, 808-damping spring upper support, 809-guide rod limiting part, 810-buffer cushion block, 811-valve core cover plate, 812-connecting bolt, 813-valve core, 814-buffer valve seat, 815-valve seat sealing part, 816-buffer spring, 817-valve core sealing part and 818-damping spring lower support; 9-piston pump, 901-piston rod, 902-cylinder, 903-piston, 904-rodless cavity, 905-rod cavity; 10-collecting box, 101-liquid outlet cavity, 102-liquid inlet cavity.
Detailed Description
A high flow low noise piston pump as shown in figure 1. The piston pump comprises a driving device, the driving device consists of a speed changer 3 and a motor 4 for driving the speed changer 3, cranks 2 are fixedly arranged at two output shaft ends of the speed changer 3, and the cranks 2 are hinged with piston rods 901 of a piston pump 9 through corresponding connecting rods 1 and reciprocating guides 5. The piston pump 9 employs a single-rod pump to form a rod chamber and a rodless chamber. The rod cavity is respectively communicated with two one-way valves 8 which are communicated with the liquid inlet 6 and the liquid outlet 7, and the rodless cavity is also respectively communicated with two one-way valves 8 which are communicated with the liquid inlet 6 and the liquid outlet 7; at least 4 check valves 8 are connected to each piston pump 9.
In the large-flow low-noise piston pump shown in fig. 2 and 3, a motor 4 of a drive unit and a transmission 3 are connected together to form a motor transmission, two output shafts are symmetrically extended from both sides of the transmission 3, and cranks 2 are fixedly attached to both of the two output shafts. The outer end of the crank 2 is hinged with a connecting rod 1, the other end of the connecting rod 1 is hinged with a guide frame 503, two side ends of the guide frame 503 are symmetrically hinged with guide rails 501, each guide roller 502 is supported on the corresponding guide rail 501 in a rolling way, the guide rails 501 are linear rails and are parallel to each other, the two linear rails are parallel to the central line of the piston pump 9, the guide rails 501 are fixedly connected with a cylinder cover at one end of a cylinder body 902 of the piston pump 9, a piston rod 901 hermetically penetrates through the cylinder cover at the end to extend outwards, and the extending end of the piston rod 901 is connected with the guide frame 503 through a connecting shaft joint 504. The guide rail 501, the guide roller 502, the guide frame 503 and the coupling 504 constitute the reciprocating guide 5. The other end of the cylinder 902 of the piston pump 9 is fixedly connected to the tank of the header 10.
Referring to the collecting box 10 shown in fig. 4, the collecting box 10 is divided into a liquid outlet chamber 101 and a liquid inlet chamber 102, the liquid outlet chamber 101 is communicated with the liquid outlet 7, the liquid inlet chamber 6 is communicated with the liquid inlet chamber 102, and eight check valves 8 are fixedly supported on a rib plate in the middle of the collecting box 10. Eight check valves 8 are respectively communicated with the rod cavity 905 and the rodless cavity 904 of each piston pump 9 and connected to the liquid inlet 6 and the liquid outlet 7 according to the communication relationship shown in fig. 1.
As shown in fig. 5, the angle α =90 ° between the two cranks 2 in space is illustrated, so that when the crank in the vertical position rotates the connecting rod, the hinge point of the crank and the connecting rod has a larger horizontal velocity component and a larger displacement component, and the horizontal velocity component and the displacement component of the crank become smaller gradually with the rotation of the crank, and when the crank in the horizontal position rotates the connecting rod, the hinge point has a smaller horizontal velocity component and a smaller displacement component, but the horizontal velocity component and the displacement component of the crank become larger gradually with the rotation of the crank, so that the structure can balance the load of the driving device and smooth the output pulsation of the pump.
Fig. 6 shows a specific structure of the check valve, and the check valve 8 comprises a valve body 804 in the shape of a short tube, 4 support rods 805 are fixedly supported at the upper end of the valve body 804, and a limit top plate 806 is fixedly mounted at the top of the support rods 805. A buffer spring seat 803 is fixedly installed in the lower port end of the valve body 804, and a guide rod lower slide 802 is fixedly installed in the buffer spring seat 803 in the radial direction of the valve body 804.
A cushion valve seat 814 is movably supported on the inner wall of the valve body 804, the cushion valve seat 814 has an annular structure, a valve seat seal 815 is installed between the circumferential side surface of the cushion valve seat 814 and the inner wall surface of the valve body 804, and the valve seat seal 815 is an O-ring rubber seal. Four buffer springs 816 are supported between the lower end surface of the buffer valve seat 814 and the buffer spring seat 803, the buffer springs 816 are compression cylindrical springs, and the lower ends of the buffer springs 816 are located in corresponding spring holes of the buffer spring seat 803.
The sliding guide rod 801 passes through the limit top plate 806 and the guide rod lower sliding seat 802 along the center line of the valve body 804 and is supported on the valve body 804 in a sliding mode. The upper end of the sliding guide rod 801 is slidably supported in a corresponding guide rod hole of the limit top plate 806, a guide rod limiting piece 809 is fixedly installed at the top of the upper end of the sliding guide rod 801, and the guide rod limiting piece 809 may not be a separate structure but be an integral structure with the sliding guide rod 801. The lower end of the sliding guide 801 is slidably supported in a corresponding guide hole of the guide lower slide 802. A valve core 813 is sleeved at the middle section of the sliding guide rod 801, and a spring cavity is arranged at the core part of the valve core 813, and a valve core damping spring 807 is arranged in the spring cavity. The spool damper spring 807 is a compression cylinder spring, and the lower end thereof is supported on the slide guide 801 by a damper spring lower support 818, i.e., the damper spring lower support 818 is fixedly connected to the slide guide 801 or the slide guide 801 is an integral structure. The upper end of the valve core damping spring 807 supports a cushion block 810 through a damping spring upper support 808, the cushion block 810 is slidably sleeved on the sliding guide rod 801, the cushion block 810 can be movably positioned at the central position of the valve core cover plate 811, and the damping spring upper support 808 positioned in a spring cavity of the valve core 813 supports the inner side of the valve core cover plate 811. The valve core cover plate 811 is fixedly connected to the valve core 813 by a connecting bolt 812, and the cushion block 810 is made of an elastic material, such as a nylon block, a rubber block, and the like. The other end of the valve core 813 is hermetically and slidably sleeved with the sliding guide rod 801, a valve core seal 817 is installed between the valve core 813 and the sliding guide rod 801, and the valve core seal 817 is also an O-shaped rubber sealing ring.
When the valve core 813 moves downwards and is closed, the descending speed is increased because the fluid pressure difference between two ends of the valve core 813 is larger and larger. When the sealing surface of the valve element 813 is attached to the sealing surface of the cushion valve seat 814 to form a sealing pair, a gap b between the lower end surface of the cushion valve seat 814 and the cushion spring seat 803 is larger than a gap a between the guide rod limiting piece 809 and the limiting top plate, wherein a =1mm and b =3mm in the embodiment; preferably b = (2-4) a.
After the valve core 813 is attached to the buffer valve seat 814 under the action of the medium fluid, the valve core 813 continues to compress the buffer spring 816 under the pushing of the medium fluid and through the buffer valve seat 814, when the guide rod limiting piece 809 collides with the limiting top plate 806, the sliding guide rod 801 stops moving downwards along with the valve, the downward speed and the pushing of the valve core 813 begin to compress the valve core damping spring 807 through the valve core cover plate 811 and the damping spring upper support 808, and at the moment, the valve core damping spring 807 and the damping spring 816 play a role together to further absorb vibration and reduce vibration, so that the impact vibration and the impact noise of the valve core and the valve seat are reduced to the maximum extent.
When the check valve is opened, the valve core 813 moves upwards under the action of medium fluid, and the pressure difference between two sides of the valve core 813 is reduced because the flow passage in the check valve is gradually increased. The upward speed of the valve core gradually becomes slower. When the cushion block 810 hits the inner side of the top plate 806, the cushion block 810 first performs a vibration damping and absorbing function. The valve core 813 then performs the vibration damping and absorbing function through the vibration damping spring lower support 818 and the valve core vibration damping spring 807.
The above description only illustrates a preferred embodiment of the present invention, but the present invention is not limited to the above embodiments, and the modifications and changes made without departing from the basic principles of the present invention are within the protection scope of the present invention.
Claims (10)
1. The utility model provides a large-traffic low noise piston pump, includes drive arrangement to and the piston pump (9) of being connected with drive arrangement transmission, its characterized in that: the driving device is in transmission connection with at least one piston pump (9); the extending end of a piston rod (901) of each piston pump (9) is connected with a reciprocating guide (5), and a crank (2) fixedly arranged at the output end of the driving device is hinged with the reciprocating guide (5) through a connecting rod (1); the cranks (2) corresponding to the piston pumps (9) are arranged in a staggered way; a rodless cavity (904) of the piston pump (9) is respectively communicated with a one-way valve (8) communicated with the liquid inlet (6) and the liquid outlet (7), and a rod cavity (905) of the piston pump (9) is also respectively communicated with a one-way valve (8) communicated with the liquid inlet (6) and the liquid outlet (7); the check valve (8) comprises a valve body (804), a buffer valve seat (814) is movably supported in the valve body (804), a buffer spring seat (803) is also fixedly arranged on the valve body (804), and a buffer spring (816) is arranged between the buffer valve seat (814) and the buffer spring seat (803); a limiting top plate (806) is fixedly supported on the valve body (804), a sliding guide rod (801) is movably supported on the valve body (804) through the limiting top plate (806), a guide rod limiting piece (809) is fixedly arranged at the upper end of the sliding guide rod (801), and the guide rod limiting piece (809) corresponds to the limiting top plate (806) in position; a valve core (813) is movably sleeved on the sliding guide rod (801), a spring cavity of the valve core (813) is provided with a valve core damping spring (807), one end of the valve core damping spring (807) is supported with a buffer cushion block (810), and the other end of the valve core damping spring (807) is supported on the sliding guide rod (801); the sealing surface of the buffer valve seat (814) is opposite to the sealing surface of the valve core (813), and when the sealing surface of the buffer valve seat (814) is attached to the sealing surface of the valve core (813), the clearance b between the buffer valve seat (814) and the buffer spring seat (803) is larger than the clearance a between the guide rod limiting piece (809) and the limiting top plate (806).
2. The high flow, low noise piston pump of claim 1, characterized by: the driving device is in transmission connection with 2-6 piston pumps (9).
3. High flow rate low noise piston pump according to claim 1 or 2, characterized in that: the drive device comprises a transmission (3) for driving an electric machine (4) of the transmission (3).
4. The high flow, low noise piston pump of claim 1, characterized by: the reciprocating guide (5) comprises a guide frame (503), the guide frame (503) is supported on a guide track (501) in a sliding mode, the extending end of a piston rod (901) is fixedly connected with the guide frame (503), one end of a connecting rod (1) is hinged with the guide frame (503), the other end of the connecting rod (1) is hinged with a crank (2), and the guide track (501) is parallel to the central line of the piston pump (9).
5. High-flow low-noise piston pump according to claim 1, characterized in that the spatial angle α of the two adjacent cranks (2) is between 80 ° and 100 °.
6. The high flow, low noise piston pump of claim 1, characterized by: when the sealing surface of the buffer valve seat (814) is attached to the front surface of the valve core (813), the clearance b between the buffer valve seat (814) and the buffer spring seat (803) is 2-4 times of the clearance a between the guide rod limiting piece (809) and the limiting top plate (806).
7. The high flow, low noise piston pump of claim 1, characterized by: a guide rod lower sliding seat (802) is fixedly mounted on the buffer spring seat (803), the upper end of the sliding guide rod (801) is slidably supported on the limiting top plate (806), and the lower end of the sliding guide rod (801) is slidably supported on the guide rod lower sliding seat (802); the guide rod limiting piece (809) is located above the limiting top plate (806).
8. High flow low noise piston pump according to claim 1, 6 or 7, characterized in that: one end of the valve core damping spring (807) is supported on the sliding guide rod (801) through a damping spring lower support (818), the other end of the valve core damping spring (807) is supported with a cushion block (810) through a damping spring upper support (808), and the cushion block (810) is sleeved on the sliding guide rod (801) in a sliding mode; the valve core (813) is fixedly connected with a valve core cover plate (811), the buffer cushion block (810) is movably arranged at the center of the valve core cover plate (811), and the upper support (808) of the damping spring is supported on the inner side of the valve core cover plate (811).
9. High flow low noise piston pump according to claim 1, 6 or 7, characterized in that: a valve seat sealing member (815) is arranged between the buffer valve seat (814) and the valve body (804); and a valve core sealing member (817) is arranged between the valve core (813) and the sliding guide rod (801).
10. The high flow, low noise piston pump of claim 9, wherein: the valve seat sealing piece (815) and the valve core sealing piece (817) are O-shaped sealing rings; the cushion pad block (810) is an elastic pad block; the limit top plate (806) is fixedly supported on the valve body (804) through a support rod (805).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920084855.5U CN210049997U (en) | 2019-01-18 | 2019-01-18 | High-flow low-noise piston pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920084855.5U CN210049997U (en) | 2019-01-18 | 2019-01-18 | High-flow low-noise piston pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210049997U true CN210049997U (en) | 2020-02-11 |
Family
ID=69376349
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920084855.5U Expired - Fee Related CN210049997U (en) | 2019-01-18 | 2019-01-18 | High-flow low-noise piston pump |
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| Country | Link |
|---|---|
| CN (1) | CN210049997U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109519353A (en) * | 2019-01-18 | 2019-03-26 | 东台市东方船舶装配有限公司 | Big flow low noise piston pump |
-
2019
- 2019-01-18 CN CN201920084855.5U patent/CN210049997U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109519353A (en) * | 2019-01-18 | 2019-03-26 | 东台市东方船舶装配有限公司 | Big flow low noise piston pump |
| CN109519353B (en) * | 2019-01-18 | 2024-04-09 | 东台市东方船舶装配有限公司 | High-flow low-noise piston pump |
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Granted publication date: 20200211 Termination date: 20210118 |