CN212168295U - Straight cylinder type high-pressure cleaning equipment and high-pressure cleaning system - Google Patents

Abstract

The utility model discloses a straight cylinder high pressure cleaning equipment and high pressure cleaning system, wherein, straight cylinder high pressure cleaning equipment includes the shell, drive structure, the circuit structure, fluid inlet, fluid outlet and by the reciprocal linear motion of drive structure drive with follow fluid inlet with fluid introduction pressurize chamber and pressurization back by fluid outlet exhaust piston, the shell has the cavity and follows the straight section of thick bamboo of sharp extension for inside, the axis of shell and the power output shaft's of drive structure axis and the axis of piston are coaxial or parallel. The shell of the scheme is in a straight cylinder shape, so that the occupied space can be effectively reduced, and the miniature production of equipment is facilitated. When the hand-held type hand-held device is used, a user can hold any position of the shell, so that the load of the palm and the arm of an operator can be effectively reduced, and the use is convenient; meanwhile, one-hand operation is conveniently realized, the operation flexibility is greatly improved, two-hand operation is not needed, one hand is liberated to carry out other operations, and the design is more humanized.

Description

Straight cylinder type high-pressure cleaning equipment and high-pressure cleaning system

Technical Field

The utility model relates to a cleaning equipment, especially straight cylinder high pressure cleaning equipment and high pressure cleaning system.

Background

The high-pressure cleaning machine is a device which utilizes a reciprocating piston to compress liquid in a cylinder body so as to pressurize the liquid to form high-pressure water flow to clean objects, and can be used for cleaning automobiles, floors, wall surfaces, doors and windows and the like. With the continuous improvement of the living standard of people, the high-pressure cleaning machine is favored by more and more families.

The traditional high-pressure cleaning machine mainly refers to a hand-push type high-pressure cleaning machine, the cleaning machine adopts a trolley and other modes to move a heavy machine body, and due to the fact that the size and the weight are large, the portability is poor, the application range is limited to a certain extent, and a lot of inconvenient places still exist during operation.

In order to meet the requirements of users on household and outdoor activities, the cleaning is convenient and the machine is convenient to carry. At present, handheld high-pressure cleaning machine powered by single direct current battery pack is available on the market

However, in the prior art hand-held cleaning machines, such as the structure disclosed in the application No. 201810747334.3, the casing of the machine usually has a gun-shaped appearance, which results in a large overall size of the high pressure cleaning machine and is inconvenient for miniaturization and portability.

Meanwhile, during operation, as the operator holds the handle at the near end of the shell and the whole cleaning machine is longer after the joint is connected, the gravity center of the whole cleaning machine is positioned in front of the handle, so that the hand and the arm of the operator need to bear larger load, the difficulty of one-hand operation is increased, and the cleaning machine is obviously unfriendly for the long-time use of the operator.

In order to reduce the difficulty of one-hand operation, the second handle is added, the size of the equipment is further increased after the second handle is added, and the size of the cleaning machine is further increased.

Finally, two-hand operation is required during operation, which is obviously not beneficial to freeing the two hands of the operator, and compared with one-hand operation, the two-hand operation has certain limitation on the use angle and poor use flexibility.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a straight cylinder high pressure cleaning equipment and high pressure cleaning system in order to solve the above-mentioned problem that exists among the prior art.

The purpose of the utility model is realized through the following technical scheme:

the straight-tube type high-pressure cleaning equipment comprises a shell, a driving structure, a circuit structure, a fluid inlet, a fluid outlet, a fluid inlet and outlet control mechanism and a piston, wherein fluid is allowed to enter a pressurizing cavity only from the fluid inlet and is discharged from the fluid outlet, the piston is driven by the driving structure to do reciprocating linear motion so as to introduce the fluid into the pressurizing cavity from the fluid inlet and discharge the pressurized fluid from the fluid outlet, the shell is a straight tube which is provided with a cavity inside and extends along a straight line, the axis of the shell is coaxial or parallel with the axis of a power output shaft of the driving structure, and the axis of the power output shaft is coaxial or parallel with the axis of the piston.

Preferably, in the straight-tube type high-pressure cleaning device, the cross section of the housing is a circle or an ellipse or a regular polygon with the number of sides not less than 4.

Preferably, in the straight-tube high-pressure cleaning device, a start-stop button for starting and stopping the motor in the driving structure is arranged at the end face of the proximal end of the housing.

Preferably, in the straight-tube high-pressure cleaning device, an electrical connection interface for connecting an external power supply and the circuit structure is arranged at the proximal end face of the housing.

Preferably, in the straight-tube high-pressure cleaning device, the axes of the circuit board and the battery in the circuit structure are parallel to or coaxial with the axis of the housing.

Preferably, in the straight-barrel type high-pressure cleaning device, the circuit board is close to the end plate at the proximal end of the shell, and the battery is located between the circuit board and the motor.

Preferably, in the straight-tube type high-pressure cleaning device, the motor in the driving structure moves in the annular cam groove through the ball or the roller pin, and the distance from the ball or the roller pin to the motor is continuously changed to switch the rotary motion of the rotating shaft of the motor into the linear motion of the piston.

Preferably, in the straight-tube type high-pressure cleaning device, the fluid inlet is connected with a first one-way valve which allows fluid to flow from the fluid inlet to the pressurizing chamber, and the fluid outlet is connected with a second one-way valve which allows fluid to flow from the pressurizing chamber to the fluid outlet.

Preferably, in the straight-tube high-pressure cleaning apparatus, the fluid inlet may be provided at a peripheral wall or a proximal end surface of the housing and may be provided with a pipe joint.

Preferably, in the straight-cylinder high-pressure cleaning device, the fluid outlet is provided with a cleaning nozzle or an outlet pipe joint.

Preferably, in the straight-tube high-pressure cleaning device, an elastic member for driving the piston to return after extending forward is arranged in the inner cavity of the piston.

Preferably, in the straight-tube high-pressure cleaning device, the piston is arranged in a guide sleeve, and the piston is connected with the guide sleeve in a sliding or rolling manner.

The high-pressure cleaning system comprises any one of the straight-barrel type high-pressure cleaning equipment and further comprises a water source connected with the fluid inlet.

The utility model discloses technical scheme's advantage mainly embodies:

1. the axial line of the motor and the axial line of the piston are parallel or coaxial with the axial line of the shell, so that the size of the inner cavity of the shell can be reduced to the maximum degree. When the hand-held type hand-held device is used, a user can hold any position of the shell, so that the load of the palm and the arm of the operator can be effectively reduced, and the use is convenient; meanwhile, one-hand operation is conveniently realized, the operation flexibility is greatly improved, two-hand operation is not needed, one hand is liberated to carry out other operations, and the design is more humanized.

2. The appearance of the whole equipment is in a cylinder shape, the appearance is attractive, the size is small, the carrying is convenient, the storage is easy, the use is convenient, and the market popularization prospect is great.

3. The overall arrangement of the motor, the storage battery, the circuit board, the power connection interface and the start-stop button in the whole scheme effectively facilitates wiring on one hand, and on the other hand, the structure can be more compact, so that the space is saved, and the miniature production of equipment is facilitated.

4. The driving mode of this scheme piston has multiple realization form, can select according to the application needs of difference is nimble to when adopting inclined end face annular cam groove and ball or kingpin complex structure, can reduce the required installation space of piston and drive structure by the maximum possible, can realize many piston drives effectively through a power supply simultaneously, can be very big adjust the pressure boost ability of equipment as required, thereby improve the cleaning performance.

5. The piston of the scheme is reset by the aid of the embedded spring, so that the overall structure is more compact, the installation space required by the piston driving structure is reduced, occupied inner space of the shell is reduced, and favorable conditions are provided for realizing a multi-piston structure.

6. The piston and the shell or the guide sleeve or the cylinder body are in rolling connection, and the rolling connection can effectively reduce the friction force between the piston and the shell or the straight cylinder, reduce the abrasion and the heating between parts, prolong the service life and is beneficial to reducing the heat generated in the equipment; on the other hand, the balls or the rolling needles slide in the guide grooves, so that the autorotation of the piston can be fully limited, the interference of the autorotation of the piston on a driving structure is avoided, and the reliability and the stability of the driving are effectively ensured.

7. The fluid inlet of the scheme is arranged at the proximal end face of the shell, and when the fluid inlet is connected with an external fluid supply pipeline, the whole pipeline is positioned behind the holding position of an operator, so that the interference on the movement and operation of the operator is reduced to the minimum, and the operability is greatly improved. And because the connecting point with the external pipeline is positioned at the rear part of the whole equipment, the load of the gravity of the external pipeline on an operator can be reduced to the minimum, the operation flexibility is greatly improved, the operation difficulty is reduced, and the long-time use of the operator is facilitated.

8. The fluid inlet is located at the near end of the shell, when the fluid inlet and outlet control mechanism are connected through the fluid channel, the fluid channel can be arranged around the periphery of the motor and the battery in a surrounding mode, water cooling of the motor and the battery can be effectively achieved, air cooling can be achieved without arranging a vent hole in the shell, the IP protection grade of the whole structure can be greatly improved, therefore, the sealing structure of the shell can be combined to enable the waterproof grade of the whole equipment to reach IPX7 grade, even IPX8 grade, the application range of the whole equipment is wider, and the whole equipment can be used even underwater.

9. This scheme is provided with the air vent simultaneously on the shell and uses with the water-cooling structure cooperation, in the use scene that requires less to the IP protection, can increase heat dispersion effectively, and the design degree of difficulty of air vent can greatly reduce simultaneously.

10. The design of the pipe joints and the outlet pipe joints at the two ends of the shell can be conveniently connected with various pipelines, so that the requirement of various low-pressure water pressurization service environments can be met.

Drawings

Fig. 1 is a cross-sectional view of the present invention (with the structure for supporting the motor, battery and circuit board hidden);

fig. 2 is a front view of the present invention (the structure of the housing, the storage battery, the circuit board, etc. are hidden in the figure);

FIG. 3 is a partial cross-sectional view of the fluid inlet and outlet control mechanism, cylinder and piston area of the present invention;

FIG. 4 is a partial cross-sectional view of the present invention with a pipe connection and a cleaning spray head or outlet pipe connection;

fig. 5 is a cross-sectional view of the fluid inlet of the present invention at the proximal end face;

fig. 6 is a cross-sectional view of the fluid inlet of the present invention positioned at the proximal end face and having a connection structure with a pipe at both ends;

fig. 7 is a partial cross-sectional view of the drive structure and piston, valve body area of the present invention;

fig. 8 is a schematic diagram of a first possible driving manner of the present invention;

fig. 9 is a perspective view of a driving member in a first possible driving manner according to the present invention;

fig. 10 is a schematic diagram of a third possible driving method of the present invention (an enlarged view of the area a in fig. 7;

fig. 11 is a perspective view of a piston in a third possible driving manner of the present invention;

fig. 12 is a schematic diagram of a fourth possible driving manner of the present invention;

fig. 13 is a cross-sectional view of the rolling connection of the piston position and the guide sleeve of the present invention;

fig. 14 is a cross-sectional view of the valve body of the present invention having a multi-cylinder structure;

fig. 15 is a schematic view of the water-cooled structure of the present invention.

Detailed Description

Objects, advantages and features of the present invention will be illustrated and explained by the following non-limiting description of preferred embodiments. These embodiments are merely exemplary embodiments for applying the technical solutions of the present invention, and all technical solutions formed by adopting equivalent substitutions or equivalent transformations fall within the scope of the present invention.

In the description of the embodiments, it should be noted that the terms "center", "upper", "lower", "left", "right", "front", "rear", "vertical", "horizontal", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the devices or elements referred to must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. In the description of the embodiment, the operator is used as a reference, and the direction close to the operator is a proximal end, and the direction away from the operator is a distal end.

The following describes the straight-tube type high-pressure cleaning apparatus disclosed in the present invention with reference to the accompanying drawings, as shown in fig. 1, which includes a housing 1, a fluid inlet 4, a fluid outlet 5, a pressurizing chamber 6, a piston 7, a driving structure 2 and a circuit structure 3.

The housing 1 is used for providing an installation space, and may be made of various feasible materials, such as a straight cylinder made of plastics, metals and the like and having a cavity inside and extending along a straight line, and the straight cylinder may be integrally formed in an injection molding manner, or formed by assembling two semicircular components, or formed by assembling a plurality of sections of pipe fittings in a screwing manner, or welding, or gluing, or interference fit manner.

The cross section of the housing 1 (the cross section obtained by cutting with a plane parallel to the axis of the housing 1 as a cutting plane) may be in various feasible shapes, for example, the cross section of the housing 1 is a circle or an ellipse or a regular polygon with the number of sides not less than 4, preferably, the cross section of the straight cylinder is a circle, and the pipe diameters of different areas of the housing 1 may be the same or different, and are specifically designed according to the required internal structure.

As shown in fig. 1, the housing 1 is provided with a fluid inlet 4 and a fluid outlet 5, the fluid inlet 4 may be a screw hole or a through hole on the housing 1, or the fluid inlet 4 is a tubular body extending from the outer surface of the housing 1 inward into the inner cavity thereof for a certain length or extending from the outer wall of the housing 1 outward vertically for a certain length, the fluid inlet 4 is connected to the pressurizing chamber 6 so that the external fluid can enter the pressurizing chamber 6, the pressurizing chamber 6 is connected to the fluid outlet 5, and the volume colloid of the pressurizing chamber is increased and decreased by the reciprocating movement of the piston 7 so that the external fluid is introduced into the pressurizing chamber 6 through the fluid inlet 4 and is ejected from the fluid outlet 5 after being pressurized.

While the fluid inlet 4 can be arranged at any position of the housing 1, two preferred positions will be described below, in embodiment 1, the fluid inlet 4 is arranged on the side wall 11 of the housing 1 and close to the far end of the housing 1; in embodiment 2, the fluid inlet 4 is provided at the end surface of the proximal end of the housing 1 as an example.

As shown in fig. 1, the position of the fluid outlet 5 can be any position on the housing 1, preferably, the axis of the fluid outlet 5 can be parallel to the axis of the housing 1, and in a more preferred embodiment, the fluid outlet 5 is an opening at the distal end of the housing 1 or a through hole formed on the end plate 12 at the distal end of the housing 1.

Example 1

As shown in fig. 1 and 2, the fluid inlet 4 and the fluid outlet 5 are connected to a fluid inlet and outlet control mechanism located in the housing 1, the fluid inlet and outlet control mechanism is preferably close to the front end of the housing 1, and the fluid inlet and outlet control mechanism only allows external fluid to be sucked into the pressurizing chamber 6 from the fluid inlet 4 when the piston 7 moves from the far end (the end of the whole device pointing forward when used by a user) to the near end (the end of the whole device pointing backward when used by a user) (when sucking), and fluid in the pressurizing chamber 6 cannot be discharged outwards through the fluid outlet 5; while external fluid is not allowed to be sucked into the pressurizing chamber 6 from the fluid inlet 4 when the piston 7 is moved from the proximal end to the distal end (when being pressed), and only the fluid in the pressurizing chamber 6 is allowed to be discharged outside through the fluid outlet 5.

In a possible way, the fluid inlet and outlet control mechanism comprises a one-way valve (not shown) connected to the fluid inlet 4 and allowing fluid to enter the pressurized chamber 6 from the outside and a one-way valve (not shown) connected to the fluid outlet 5 and allowing fluid to flow out of the pressurized chamber 6 and out of the fluid outlet 5, in this embodiment, the whole structure is similar to that of a syringe having a fluid inlet connected to a one-way valve and a fluid outlet connected to another one-way valve.

In yet another alternative embodiment, as shown in fig. 2-4, the fluid inlet and outlet control mechanism comprises an inlet and outlet member 70 and a valve body 80, the inlet and outlet member 70 comprises an inlet passage 701 and an outlet passage 702, the inlet passage 701 comprises a first vertical pipe 7011 and a second vertical pipe 7012, preferably, the inlet of the first passage 7011 is coaxial with the fluid inlet 4, and the first passage 7011 and the fluid inlet 4 can be connected in a sealing manner or can maintain a certain gap.

As shown in fig. 3, the discharge channel 702 comprises a third conduit 7021 and a fourth conduit 7022, preferably with parallel but not coaxial axes, which communicate end to end through an articulation channel (not marked in the figures), the axis of the third conduit 7021 being parallel to the axis of the piston 7 and perpendicular to the first conduit 7011, the outlet of the fourth conduit 7022 being coaxial with the axis of the fluid outlet 5, the fourth conduit 7022 preferably extending outside the fluid inlet 5 of the housing 1.

The inlet channel 701 and the outlet channel 702 may be isolated from each other or may be communicated with each other, and when the inlet channel 701 and the outlet channel 702 are communicated with each other, as shown in fig. 3, the first conduit 7011 and the third conduit 7021 are communicated with each other, the first conduit 7011 and the second conduit 7012 are distributed in a T shape, the communication holes of the first conduit 7011 and the third conduit 7021 are sealed by a plug 703, and the plug 703 may be screwed with the communication holes.

As shown in fig. 3 and 4, the inlet and outlet member 70 is coaxially connected to the valve body 80, and is assembled into a whole by flange connection or screw connection, a passage 801 communicating the inlet passage 701 and the pressurizing chamber 6 is formed on the valve body 80, a first check valve 20 allowing fluid to flow from the inlet passage 701 to the pressurizing chamber 6 is disposed on the passage 801, a passage 802 communicating the outlet passage 702 and the pressurizing chamber 6 is further disposed on the valve body 80, and a second check valve 30 allowing fluid to flow from the pressurizing chamber 6 to the fluid outlet is disposed in the passage 802. Of course, the first check valve 20 may be other structures capable of realizing one-way control of fluid, which are known in the art and not described herein.

Of course, in other embodiments, the access member 70 may be omitted, such that the inlet of the passageway 801 of the valve body 80 is coaxial with and sealingly connected to or maintains a gap with the fluid inlet 4, and the outlet of the passageway 802 of the valve body 80 is coaxial with and sealingly connected to or maintains a gap with the fluid outlet 5.

In actual use, the external fluid supply line may directly pass through the fluid inlet 4 and connect with the first conduit 7011 of the access member 70 (when the access member 70 is not provided, the external fluid supply line is in sealing connection with the inlet of the passage 801 of the valve body 80), and a gap may be maintained between the fluid inlet 4 and the first conduit 7011 or the passage 801. Of course, the external fluid supply line may also be directly connected to the fluid inlet 4, for example, by screwing or interference fit, in which case the fluid inlet 4 and the inlet of the first conduit 7011 or the channel 801 need to be hermetically connected.

Further, in order to simplify the sealing structure and facilitate the connection, as shown in fig. 3, the first pipe 7011 or the channel 801 is detachably connected to a pipe joint 40, the pipe joint 40 and the first pipe 7011 or the channel 801 may be connected by a screw thread or an interference fit, and an outer wall of the pipe joint 40 and an inner wall of the first pipe 7011 or an inner wall of the channel 801 are sealed by a sealing ring, the pipe joint 40 passes through the fluid inlet 4 from the inside of the housing 1 and extends to the outside of the housing 1, and an inlet end thereof faces a proximal end of the housing 1, and in actual use, an external fluid supply pipeline is directly connected to the pipe joint 40.

As shown in fig. 2 and 4, a cleaning nozzle or an outlet pipe joint 400 is detachably connected to an outlet of the fourth pipe 7022 of the access member 70, and the cleaning nozzle or the outlet pipe joint 400 may be in threaded connection with the fourth pipe 7022 or may be in threaded connection with the fourth pipe 7022 by a bolt. The cleaning spray head or outlet pipe fitting 400 may also be removably connected to the outlet of the passageway 802 of the valve body when the access member 70 is not present. Of course, the cleaning nozzle or the outlet pipe joint 400 may also be directly connected to the fluid outlet, that is, the cleaning nozzle or the outlet pipe joint is directly connected to the front opening or the through hole (fluid outlet) of the housing 1, and when the fluid outlet 5 is a through hole on the distal end panel 12, the outlet of the fourth pipe 7022 of the access member or the channel 802 of the valve body 80 is hermetically connected to the fluid outlet 5.

Meanwhile, the cleaning nozzle or outlet pipe joint 400 may be various nozzles or joints, for example, when it is a nozzle, the caliber of the liquid outlet end thereof is gradually reduced from inside to outside, i.e. it is a cone, so that the water outlet pressure can be further increased, and the cleaning effect can be improved; in other embodiments, the cleaning nozzle can be a structure similar to a shower head, which can effectively increase the cleaning area

Example 2

This embodiment differs from embodiment 1 described above in that: as shown in fig. 5, the fluid inlet 4 is disposed at the proximal end of the housing 1, preferably at the proximal end face, that is, the fluid inlet 4 includes at least one hole on the end plate 13 at the proximal end of the housing, in this case, because the fluid inlet 4 has a larger distance from the fluid inlet and outlet control mechanism at the distal end, a fluid channel 300 is further disposed between the fluid inlet 4 and the inlet of the fluid inlet and outlet control mechanism, and the fluid channel 300 is preferably disposed inside the housing 1, but may be disposed outside the housing 1 in other embodiments.

In this case, the fluid inlet 4 may also extend perpendicularly outward from the proximal end plate 13 of the housing 1 by a certain distance, thereby facilitating detachable connection with the pipe joint 40 or an external pipe. Of course, the adapter 40 may be detachably connected to the fluid channel 300 through the fluid inlet 4, or the adapter 40 may be integrally formed with the fluid channel 300 and extend directly from the inside of the housing 1 through the fluid inlet 4 to the outside of the housing 1.

In this structure, the external fluid supply line is connected to the proximal end of the housing 1, and is generally held on the outer peripheral wall of the housing 1 when operated by a user, that is, the external fluid supply line is located behind the holding position of the operator, thereby greatly reducing the interference of the external fluid supply line with the movement of the operator, and at the same time, the external fluid supply line is located at the rear end, so that the center of gravity of the entire apparatus is moved backward when operated, thereby effectively reducing the load on the operator's person, and facilitating long-term, flexible, and convenient use.

Furthermore, in addition to the pipe diameter of the pipe joint 40 being equal to that of the fluid inlet 4, as shown in fig. 6, in a further possible embodiment, the pipe diameter of the pipe joint 40 is preferably equal to and coaxial with the pipe diameter of the proximal end of the housing 1, in this case, the pipe joint 40 may even be integrally injection-molded with the housing 1, and the pipe diameter of the pipe joint 40 may be equal to that of a domestic water pipe such as a tap water pipe, a water supply pipe of a water heater, and the like, and at the same time, the inner circumferential wall and/or the outer circumferential wall of the pipe joint 40 is formed with threads, so that, when in use, the pipe joint 40 can be directly connected with the tap water pipe and the hot water pipe to achieve better use effect by increasing the water.

Of course, the pipe joint 40 may have an inner end (outlet end) corresponding to the pipe diameter of the fluid inlet 4 or the fluid channel 700 and an outer end (inlet end) corresponding to the pipe diameter of a household water pipe or other various pipes, so that pipe joints of corresponding sizes may be connected according to different applications.

Correspondingly, as shown in fig. 6, the distal end of the housing 1 is further provided with an outlet pipe joint 400, the outlet pipe joint 400 is coaxial with the housing 1, the pipe diameter of the outlet pipe joint 400 can be designed according to the requirement, and the outlet pipe joint 400 can be integrally formed with the housing 1, and of course, can be detachably connected with the housing 1 by adopting a threaded connection manner, or the outlet pipe joint 400 can be connected to the fourth channel of the access member by adopting a threaded connection manner.

Similarly, the inner end (inlet end) of the outlet pipe joint 400 is equivalent to the outlet pipe diameter of the fluid outlet 5 or the fourth channel, and the outer end (outlet end) is equivalent to the pipe diameter of a household water pipe or other various pipelines, so that the outlet pipe joint with corresponding size can be connected according to different application occasions.

The whole equipment can be connected in any pipeline structure which needs to pressurize and output the fluid according to the use requirement, for example, the whole equipment is connected in an indoor water supply pipeline of a high-rise household, namely, the fluid inlet 4 is directly or indirectly connected with the outlet of one pipeline, and the fluid outlet 5 is directly or indirectly connected with the inlet of the other pipeline, so that the low-pressure water is pressurized, and the water pressure of all parts of the whole household is improved.

In the structure in which the fluid inlet is provided at the proximal end, the shape of the housing 1 is not limited to a straight tube shape, and may be other feasible shapes such as a gun shape, in which case the fluid inlet is provided at the bottom of the grip portion or toward the rear (in use, the direction toward which the water outlet is directed is the front).

As shown in fig. 1, fig. 2, fig. 4, and fig. 7, the valve body 80 is coaxially connected to a cylinder 90 fixed in the housing 1, the piston 7 is disposed in the cylinder 90 in a manner of reciprocating in a direction parallel to the axis of the cylinder 90, and the outer wall of the piston 7 is sealed with the inner wall of the cylinder 90, specifically, by a seal ring 100, the seal ring 100 may be a piston ring or other feasible seal ring, and the seal ring is preferably a Y-shaped seal ring. Meanwhile, the sealing ring 100 can move along with the piston 7, but it can also be fixed at a position without moving along with the piston 7, for example, it is located in a limited groove formed by the valve body 80 and the cylinder 90, so that the piston 7, the valve body 80, the cylinder 90 and the sealing ring 100 enclose a space as the pressurizing chamber 6, when the piston 7 moves towards the valve body, the fluid in the pressurizing chamber 6 can be compressed to discharge the flow chart from the pressurizing chamber 6.

Of course, in other embodiments, the valve body 80 may be directly and hermetically connected with the inner wall of the housing 1, and the structure and connection relationship between the piston 7 and the housing 1 may be similar to those of a medical syringe, such that the space enclosed by the piston 7, the housing 1 and the valve body 80 forms the pressurizing chamber 6.

The piston 7 is driven by a driving structure 2 arranged in the housing 1 to reciprocate in the housing 1 along the extending direction of the housing 1, and the driving structure 2 can be various feasible structures, such as an air cylinder, a hydraulic cylinder, an electric push rod and the like.

Or, in other embodiments, when the internal cavity of the housing 1 is large enough, especially when the internal diameter is large enough, the axis of the rotating shaft of the motor 21 of the driving structure 2 may be perpendicular to the axis of the housing 1, and the motor may drive the piston 7 to reciprocate through a crank-link structure, or the motor may drive a cardan shaft through a bevel gear transmission structure, a belt transmission structure, or a chain transmission structure to drive the piston, where the corresponding transmission structures are known in the art and are not described herein again.

In a preferred embodiment, the axis of the power output shaft of the driving structure 2 is parallel to or coaxial with the axis of the piston 7, specifically, as shown in fig. 7, the driving structure includes a motor 21, the motor 21 is fixed in the housing 1, the rotating shaft 211 of the motor 21 is parallel to, preferably coaxial with, the axis of the housing 1, and the rotating shaft 211 is detachably connected to the input end of a reduction box 22 through a transmission shaft which is inserted into the insertion hole of the input shaft of the acceleration box 22 and is connected with a transmission torque, as shown in fig. 2, the reduction box 22 is coaxially connected to the cylinder 90 through a connecting sleeve 500, the output shaft 221 of the reduction box 22 and the power output shaft of the driving structure 2 are connected to a driving member 23, and the driving member 23 and the piston 7 are moved in an annular cam groove on an inclined end surface or an annular cam groove on a side wall through a ball or a needle 10 to switch the rotational movement of the driving member 23 into a 7 is moved linearly.

Here, the structure of the driving member 23 for driving the pistons 7 is various, and may be reasonably selected according to the number of the pistons 7,

in the following, several embodiments of the driving member 23 driving the piston 7 will be described, taking the piston 7 as one and coaxial with the power take-off shaft as an example:

in a first possible embodiment, as shown in fig. 8 and 9, the driving member 23 is a circular shaft 231 coaxially connected to the output shaft 221 of the reduction gearbox 22, an annular cam groove 233 is formed on a circumferential wall 232 of the circular shaft 231, balls or needles 10 are disposed in the annular cam groove 233, the balls or needles 10 protrude outside the annular cam groove 233, the circular shaft 231 is coaxially inserted into a connecting groove 71 at one end of the piston 7, a limiting groove or hole 72 is formed on a groove wall of the connecting groove 71, and the balls or needles 10 are limited in the limiting groove or hole 72, so that when the circular shaft 231 rotates, the balls or needles 10 move in the annular cam groove 233 and continuously shift forward and backward positions, thereby driving the piston 7 to reciprocate.

In a second possible embodiment, the piston 7 may be inserted into a slot of the circular shaft 231, and correspondingly, the annular cam groove 233 is formed on the outer wall of the piston 7, and a limit groove or hole for limiting the ball or the needle is provided in the slot of the circular shaft 231.

In a third possible embodiment, the driving member 23 is also a circular shaft and is coaxial with the piston 7, the driving member 23 being screwed to the piston (one of the driving member 23 and the piston 7 is internally threaded and one is externally threaded), while the piston 7 cannot spin, for example by preventing it from rotating by means of a rolling connection with the cylinder or guide sleeve as described below.

In a fourth practical example, as shown in fig. 10 and 11, the driving element 23 is a swing arm 234, one end of the swing arm 234 is vertically connected to the output shaft 221 of the reduction gearbox 22, one end of the swing arm 234 facing the piston is provided with a locking groove 235, a ball or needle roller 10 is disposed in the locking groove 235, the end surface 71 of the piston 7 facing the swing arm 234 is an inclined surface, an annular groove is formed on the inclined surface, the annular groove on the inclined surface is the annular cam groove 72, the annular cam groove is coaxial with the output shaft 221 of the reduction gearbox 22, the ball or needle roller 10 is limited in the annular cam groove 72, and in order to avoid interference between the swing arm 234 and the inclined surface of the piston 7, a supporting pillar (not shown in the figure) is further formed at the end surface of the swing arm 234, so that the rotation of the swing arm 234 drives the ball or needle roller 10 to roll in the annular cam groove 72, pushing the piston 7 to move in a direction away from the motor 21. Meanwhile, the groove bottom surface of the circular groove can be a plane or a curved surface, and different output characteristic requirements can be met by adjusting the groove bottom surface of the circular cam groove 72.

Of course, in a fifth possible embodiment, as shown in fig. 12, the driving member 23 may be a rotary disc 236, an end face 2361 of the rotary disc 236 facing the piston is formed with an annular cam groove 2362 which is the same as that of the fourth possible embodiment, a ball or a needle 10 is rollably defined on the end face of the piston 7 facing the rotary disc 236, and the ball or the needle is simultaneously located in the annular cam groove 2362, and similarly, in order to avoid interference between the piston and the rotary disc 236, an eccentric supporting column 74 may be provided on the end face of the piston 7, and a limit groove 741 for limiting the ball or the needle 10 is provided on the end face of the supporting column 74 facing the driving member 23.

In the fourth and fifth embodiments, the drive structure 2 can drive the piston 7 only in the direction away from the motor 21 to reduce the volume of the pressurizing chamber 6 and pressurize the fluid, but the motor 21 cannot effectively return the piston 7 after the forward compression, and in this case, a certain return mechanism is required to return the piston 7.

Correspondingly, as shown in fig. 7 and 12, the reset mechanism may be various elements or structures capable of deforming and accumulating force when being stressed and releasing the accumulated force and restoring the original shape when the stress is removed, for example, it may be various elastic members 50, more preferably springs, elastic sheets, etc., taking springs as an example, the springs may be sleeved on the periphery of the piston 7 and one end of the springs is fixed on the outer wall of the piston 7, and the other end abuts against or is fixed on the front end face (the end face facing the piston) of the reduction gearbox, at this time, when the piston 7 moves towards the pressurizing chamber 6 to compress the fluid therein, the springs are stretched; when the piston 7 is moved towards the motor, the spring is gradually restored, but it is still in a certain state of compression, so that a certain pulling force is applied to the piston 7, causing the balls or needles 10 to be restrained. Of course, the other end of the spring may also abut against or be fixed to the rear end face (the end face facing the piston) of the valve body 80, and the spring constantly applies a pressure to the piston 7 in the motor direction. The piston 7 comprises a cylinder 71, and an elastic piece for enabling the cylinder 71 to be in a suction position is arranged in an inner cavity of the cylinder 71.

In the above structure, the spring is located at the periphery of the piston 7, which increases a certain installation space, which is not beneficial to distributing a plurality of pistons in a limited space so as to increase pressure, therefore, in a more preferred structure, as shown in fig. 12, a limit groove 76 parallel to the axis 75 of the piston is formed on the piston 7, the limit groove 76 preferably works with the axis 75 and is internally provided with a spring having an axis parallel to or coaxial with the axis, one end of the spring abuts against the groove bottom of the limit groove 76, and the other end abuts against the rear end face of the valve body 80, so that the installation space required by the spring can be saved, which is beneficial to creating favorable conditions for increasing a plurality of pistons or realizing miniaturization of the whole structure.

Further, when the number of the pistons 7 is plural, that is, at least 2, preferably 2 to 6, their axes are parallel to and not coaxial with the axis of the power pivot of the drive mechanism 2, they are distributed at equal intervals, and, in order to be installed in the same space, the size of each piston 7 is reduced relative to that of the piston in the single piston structure.

At this time, some embodiments in the above-mentioned single piston 7 driving structure are inconvenient to use, so the preferred implementation is: in the manner of the fifth possible embodiment described above, that is, the driving member 23 is a rotating disc 236, the rotating disc 236 is sized such that its front end surface (end surface facing the piston) can cover all the pistons 7, that is, the projection of each piston 7 on the projection plane perpendicular to the front end surface can all fall on the front end surface of the rotating disc 236, the end surface 2361 of the rotating disc 236 facing the pistons 7 is an inclined plane and is formed with an annular cam groove 2362, a ball or needle roller 10 is rollably defined on the end surface of each piston 7 facing the rotating disc 236, the corresponding ball or needle roller of each piston 7 is located in the annular cam groove 2362, and the ball or needle roller 10 on different pistons 7 are distributed at different positions of the annular cam groove 2362, so that the lengths of at least some of the pistons 7 need to be different. Also, in order to avoid interference between the pistons and the rotary disk 236, a supporting column (not shown) may be provided on an end surface of the piston 7, so that a plurality of pistons 7 may be moved simultaneously when the rotary disk 236 rotates, thereby implementing a multi-piston drive.

Of course, in other possible embodiments, the driving member 23 may be a gear wheel, which is engaged with a plurality of transmission gears, and each transmission gear and the piston 7 are provided with the structures of the first to third possible embodiments, but such structures obviously require more space, which is not favorable for miniaturization of the device.

Furthermore, since there is a significant amount of sliding friction between the piston 7 and the inner wall of the cylinder 90 or housing 1 during reciprocation, which is clearly disadvantageous for the extension of the useful life of the parts and for heat dissipation within the housing, it is clearly necessary in a more preferred embodiment to have rolling friction between the piston 7 and the surfaces of the parts it contacts to reduce friction.

Then, when the cylinder 90 is provided, as shown in fig. 13, a guide sleeve 60 is further provided in the cylinder 90, an anti-rotation structure is provided between the guide sleeve 60 and the cylinder 90, the piston 7 is provided in the guide sleeve 60, a hole wall of a central hole of the guide sleeve 60 is a surface surrounding an outer periphery of the piston 7, an anti-rotation structure for preventing the piston 7 from rotating is provided between the piston 7 and the guide sleeve 60, the anti-rotation structure includes at least one, preferably a plurality, more preferably at least three, and polygonal guide grooves 601 provided on an inner wall of the guide sleeve 60 and extending in parallel to an axis of the guide sleeve 60, a stopper hole or groove 73 corresponding to each position of the guide grooves 601 is formed on an outer peripheral wall of the piston 7, and the number of the stopper holes or grooves corresponding to each guide groove 601 on the piston 7 is plural, a ball or roller 200 is defined in the limiting hole or groove 73, and the ball or roller 200 is simultaneously inserted into the corresponding guide groove 601 and maintains a micro gap between the inner wall of the guide sleeve 60 and the outer wall of the piston 7, thereby realizing the rolling connection between the piston 7 and the guide sleeve 60.

Of course, when the piston 7 is directly connected to the cylinder 90 or the inner wall of the housing 1, the hole wall of the central hole of the cylinder 90 through which the piston 7 passes or the inner wall of the housing 1 is a surface surrounding the outer periphery of the piston 7, and the guide groove 601 is disposed on the inner wall of the cylinder 90 or the inner wall of the housing 1.

In addition, when there are a plurality of pistons 7, as shown in fig. 14, through holes 901 corresponding to each piston 7 are formed in the cylinder 90, and at least three guide grooves 902 are formed in the hole wall of each through hole 901, in this case, each piston 7 may be sealingly connected to the hole wall of the through hole in which it is located by a seal ring (not shown). Of course, the outer contour of the cylinder body may not be circular, and a certain avoiding groove may be formed on the surface of the cylinder body as required to reduce the occupied space and weight.

As shown in fig. 1, the motor 21 may be powered and start/stop controlled by various known circuit structures 3 including a power supply circuit and a control circuit, where the power supply circuit may be configured to supply power to the motor 21 by connecting an external power supply (commercial power, a dc power supply, etc.), or may be configured to supply power to the motor 21 by a battery 31 (a dry battery, a storage battery); in a preferred embodiment, the power supply circuit has a power supply structure for supplying power to both the commercial power and the storage battery, that is, when an external power supply is connected to the power supply circuit, the power supply circuit supplies power to the motor 21 through the external power supply and charges the storage battery at the same time, and when no external power supply is connected to the power supply circuit, the power supply circuit supplies power through the storage battery.

As shown in fig. 1, the battery 31 is disposed adjacent to the motor 21, and may be a cylindrical battery 31 with its axis coaxial or parallel with the axis of the housing 1, the battery 31 is connected to a circuit on a circuit board 32, the circuit board 32 is located at the proximal end of the housing 1 with its axis 321 parallel or coaxial with the axis of the housing. Correspondingly, the housing 1 is provided with an electrical connection interface 9 for connecting an external power source to the circuit structure 3, and the electrical connection interface 9 may be any known power source interface, such as any USB interface, more preferably a type-c interface, a lignting interface, etc., and is preferably provided on an end panel 13 at the proximal end of the housing 1.

Meanwhile, a start-stop button 8 for controlling the start and stop of the motor 21 is further arranged on the housing 1, the start-stop button 8 is connected with the circuit board 32, and preferably, the start-stop button 8 is also arranged on the end panel 13 at the proximal end of the housing 1. The overall layout structure can simplify circuit connection, and greatly saves installation space so as to facilitate miniaturization of products.

Of course, in other embodiments, the power connection interface 9 may be omitted, and especially when the power connection interface 9 is used underwater, the existence of the power connection interface 9 is obviously disadvantageous to waterproof, so that the battery can be charged by taking out the battery from the housing, which is a known technology and is not described in detail herein. Meanwhile, in other implementations, a corresponding start-stop button can be omitted, and a remote control mode is adopted to control the start and stop of the motor, for example, the start and stop of the motor is controlled by a remote control system of a conventional internet of things system such as infrared remote control, wireless communication or bluetooth communication, or even the start and stop of the motor can be controlled by a language control mode, and the specific implementation structures of the control modes such as remote control, language control and the like are known technologies, and are not innovation points of the scheme, and are not described herein.

Since the battery 31 and the motor 21 are located in a small space of the housing, the battery 31 and the motor 21 need a certain cooling structure to dissipate heat during use, for example, in a feasible manner, a vent hole corresponding to the position of the motor 21 and/or the battery 31 is provided on a side wall of the housing 21, so that heat can be dissipated through airflow.

However, in this configuration, the overall apparatus is relatively low in water resistance rating and therefore cannot be used in a wet or underwater environment.

Therefore, in a more preferable mode, it is obviously more desirable to use water cooling, so that, as shown in fig. 15, when the fluid connector 4 is disposed at the proximal end face of the housing 1, the fluid inlet 4 is connected with a fluid pipeline 70, in this case, the fluid pipeline 70 can be arranged around the motor 21 and the battery 31, for example, the fluid pipeline 70 is spirally wound around the outer peripheries of the motor 21 and the outer machine 31, or the fluid pipeline 70 has a circular fluid channel around the outer peripheries of the motor 21 and the battery 31, so that the motor 21 and the battery 31 can be effectively cooled by water through the fluid pipeline 70, in this case, the vent hole on the housing 1 can be eliminated, and thus, in combination with a certain sealing structure, a sufficient waterproof level can be achieved.

Of course, in other embodiments, in addition to the water cooling structure, an air cooling structure may be retained, that is, a corresponding vent hole may be retained on the housing 1.

The present disclosure further discloses a high pressure cleaning system, which includes the straight-barrel type high pressure cleaning apparatus described in the above embodiments, and further includes a water source connected to the fluid inlet 4, where the water source may be a tap connected through a hose, and the water source is connected to the fluid inlet through a liquid supply pipeline.

The utility model has a plurality of implementation modes, and all technical schemes formed by adopting equivalent transformation or equivalent transformation all fall within the protection scope of the utility model.

Claims (13)

1. Straight cylinder type high-pressure cleaning equipment comprises a shell (1), a driving structure (2), a circuit structure (3), a fluid inlet (4), a fluid outlet (5), a fluid inlet and outlet control mechanism allowing fluid to enter a pressurizing cavity only from the fluid inlet (4) and be discharged from the fluid outlet (5), and a piston (7) driven by the driving structure (2) to do reciprocating linear motion so as to introduce the fluid into the pressurizing cavity (6) from the fluid inlet (4) and discharge the fluid from the fluid outlet (5) after pressurization, and is characterized in that: the shell (1) is a straight cylinder which is provided with a cavity inside and extends along a straight line, the axis of the shell (1) is coaxial or parallel with the axis of a power output shaft of the driving structure (2), and the axis of the power output shaft is coaxial or parallel with the axis of the piston (7).

2. The straight-barrel high-pressure cleaning apparatus according to claim 1, wherein: the section of the shell (1) is circular or oval or regular polygon with the number of sides not less than 4.

3. The straight-barrel high-pressure cleaning apparatus according to claim 1, wherein: and a start-stop button (8) for starting and stopping a motor (21) in the driving structure (2) is arranged at the end face of the near end of the shell (1).

4. The straight-barrel high-pressure cleaning apparatus according to claim 1, wherein: and an electric connection interface (9) for connecting an external power supply and the circuit structure (3) is arranged at the end face of the near end of the shell.

5. The straight-barrel high-pressure cleaning apparatus according to claim 1, wherein: the axes of the circuit board and the battery in the circuit structure (3) are parallel or coaxial with the axis of the shell.

6. The straight-barrel high-pressure cleaning apparatus according to claim 5, wherein: the circuit board is proximate to an end plate of the housing proximal end, and the battery is located between the circuit board and the motor.

7. The straight-barrel type high-pressure cleaning apparatus according to any one of claims 1 to 6, wherein: a motor (21) in the drive structure (2) moves in the annular cam groove through a ball or a roller pin (10) and continuously changes the distance from the ball or the roller pin to the motor (21) so as to switch the rotary motion of a rotating shaft of the motor into the linear motion of the piston (7).

8. The straight-barrel type high-pressure cleaning apparatus according to any one of claims 1 to 6, wherein: the fluid inlet is connected to a first one-way valve (20) which allows fluid flow from the fluid inlet to the pressurised chamber (6), and the fluid outlet is connected to a second one-way valve (30) which allows fluid flow from the pressurised chamber to the fluid outlet.

9. The straight-barrel type high-pressure cleaning apparatus according to any one of claims 1 to 6, wherein: the fluid inlet is located at the peripheral wall or proximal end face of the housing.

10. The straight-barrel type high-pressure cleaning apparatus according to any one of claims 1 to 6, wherein: and a cleaning spray head or an outlet pipe joint is arranged at the fluid outlet (5).

11. The straight-barrel type high-pressure cleaning apparatus according to any one of claims 1 to 6, wherein: an elastic piece (50) for driving the piston (7) to reset after extending forward is arranged in the inner cavity of the piston (7).

12. The straight-barrel type high-pressure cleaning apparatus according to any one of claims 1 to 6, wherein: the outer wall of the piston (7) is connected with the inner wall of the valve body or the guide sleeve (60) or the shell in a sliding and/or rolling way.

13. High pressure cleaning system, its characterized in that: a straight-barrel high-pressure cleaning apparatus comprising any one of claims 1 to 12, further comprising a water source connected to said fluid inlet (4).

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