CN218981969U - Handheld high-pressure cleaning machine - Google Patents

Abstract

The utility model relates to a handheld high-pressure cleaning machine, which comprises a handheld spray gun shell, a pump body, a transmission mechanism and a motor, wherein the pump body, the transmission mechanism and the motor are arranged in the handheld spray gun shell; the handheld spray gun shell is provided with a water flow nozzle; the pump body comprises a high-pressure chamber, a plunger, a water inlet channel and a water outlet channel; the transmission mechanism comprises a speed reducer, and the motor is connected with the speed reducer and drives the plunger to reciprocate relative to the high-pressure chamber; the motor is configured as an outer rotor brushless motor, the size of the motor in the axial direction of a power output shaft of the motor is 42-55mm, and the size of the motor from the rear edge of the motor to the front edge of the plunger in the axial direction of the power output shaft of the motor is 95-110 mm. According to the utility model, the outer rotor brushless motor is adopted, the pump body and the transmission mechanism are reasonably arranged, and on the premise of meeting the performance of the whole machine, the high pressure, the high flow, the high efficiency, the small volume, the light weight and the portability of the handheld cleaning machine can be realized, the operation comfort of the handheld cleaning machine is improved, and the cost is low, the operation is convenient and labor-saving.

Description

Handheld high-pressure cleaning machine

Technical Field

The utility model relates to the technical field of cleaning equipment, in particular to a handheld high-pressure cleaning machine.

Background

Along with the development of society and the progress of science and technology, the handheld cleaning machine is used as a cleaning device and is more and more widely applied to the life of people, so that great convenience is brought to the life of people. The hand-held cleaning machine can be used for cleaning automobiles, glass doors and windows, courtyard roads, swimming pools, pets and the like, and has the characteristics of high efficiency, safety and convenient use. The core module of the existing hand-held cleaning machine is a core pump, and comprises a plunger pump, a transmission mechanism and a motor.

In the prior art, as shown in fig. 1 and 2, a radial plunger pump is mostly adopted as a core pump of a hand-held cleaning machine below 3MPa, the pump height H of a single plunger pump with the pressure of 2.2MPa and the flow rate of 120L/H is 79.2mm, and the pump width W is 45.5mm (wherein, the dimension in the extending direction of the plunger is the height, and the dimension in the direction perpendicular to the extending direction of the plunger is the width); as shown in FIGS. 3 and 4, the pump height H of the single plunger pump with the pressure of 2.4MPa and the flow rate of 210L/H is 100.6mm, and the pump width W is 45.5mm; when improving in order to promote pressure to 5MPa and flow to 250L/H on the basis of its structure, as shown in fig. 5 and 6, the pump height H of single plunger pump, the increase range of pump width W are very big, lead to the volume too big, and weight is big, and easy to use, portability are poor, and user experience feels bad, can't satisfy the light and handy demand of hand-held type cleaning machine. In addition, as shown in fig. 7 and 8, most of the core pumps of the hand-held cleaning machines with the pressure of 3MPa or more use axial multi-plunger pumps, the pump height H of the three-plunger axial pump with the pressure of 3MPa and the flow rate of 250L/H is 67.4mm, and the pump width W is 71.4mm, but the pump length of the three-plunger axial pump is too long to meet the light and handy requirement of the hand-held cleaning machine.

Therefore, it is needed to explore how to reduce the volume of the movement pump when the pressure of the movement pump is raised to above 3Mpa and the flow rate is raised to 180-300L/h, so as to realize the characteristics of light weight, portability and light weight of the hand-held cleaning machine, so as to improve the operation comfort of the hand-held cleaning machine.

Meanwhile, the hand-held cleaning machine in the prior art has the following defects:

1) The water inlet valve of the water inlet channel is arranged along the water inlet direction, and the valve core of the water inlet valve is acted by the standby pressurized water and a larger spring force, so that the operation force required by pulling the valve core through the trigger is larger;

2) The existing motor pump driven by a planetary gear has the defects that the structure is complex, the difficulty of part processing technology is high, and the cost is high;

3) The existing single-plunger motor pump plunger bearing uses a deep groove ball bearing, as shown in figures 1, 3 and 5, when the single-plunger motor pump plunger bearing is used on a high-pressure motor pump, the size of the selected deep groove ball bearing is larger, so that the overall dimension of the whole pump body is larger, and the weight is increased;

4) The existing motor pump cavity is a closed cavity, water particles on the surface of a plunger can be gathered in the pump cavity after the machine runs for a long time, more water particles are gathered and flow into a plunger bearing, when the bearing is made of bearing steel, rust is easy to occur when the bearing is in contact with water, the bearing can be damaged after rust, and the service life of the bearing is reduced;

5) The existing motor pump motors are all inner rotor motors, and are large in size and weight, so that the size and weight of the handheld cleaning machine are increased;

6) The existing motor pump body, pump cover, gear box and pump head are made of aluminum die-casting materials when the pressure is above 3MPa, the cost is high, the weight is large, and the aluminum part is further processed after die-casting, so the cost is higher.

7) The water inlet flow passage and the pressure release valve of the high-pressure cleaning machine are arranged on the same flow passage, as shown in figure 1, the pressure release valve is partially positioned in the water inlet flow passage to form water inlet resistance, and the high-flow requirement of 300L/h is not met.

Disclosure of Invention

The utility model aims to provide a handheld high-pressure cleaning machine which is high in efficiency, small in size, light in weight and high in operation comfort.

The utility model adopts the following technical scheme:

a hand-held high-pressure cleaning machine comprises a hand-held spray gun shell, a pump body, a transmission mechanism and a motor, wherein the pump body, the transmission mechanism and the motor are arranged in the hand-held spray gun shell;

the handheld spray gun shell is provided with a water flow nozzle;

the pump body comprises a high-pressure chamber, a plunger, a water inlet channel and a water outlet channel, the plunger can do reciprocating motion relative to the high-pressure chamber so as to pressurize water flow, the water inlet channel and the water outlet channel are respectively communicated with the high-pressure chamber, and the water outlet channel is communicated with the water flow nozzle;

the transmission mechanism comprises a speed reducer, and the motor is connected with the speed reducer and drives the plunger to reciprocate relative to the high-pressure chamber;

the motor is configured as an outer rotor brushless motor, the size of the motor in the axial direction of a power output shaft of the motor is 42-55mm, and the size of the motor from the rear edge of the motor to the front edge of a plunger in the axial direction of the power output shaft of the motor is 95-110 mm.

Further, the rated pressure of the output end of the pump body is 3-7MPa, and the product of the axial dimension of the motor on the power output shaft, the dimension of the pump body on the extending direction of the plunger piston and the smaller dimension of the width and the height of the transmission mechanism is 190-230cm ³ 。

Further, the handheld spray gun shell comprises a shell and a water outlet gun barrel, and the motor, the transmission mechanism and the pump body are arranged in the shell;

the shell is provided with a gun barrel interface for connecting the water outlet gun barrel at the front end of the water outlet channel of the pump body;

in the axial direction of the power output shaft of the motor, the ratio of the length from the rear edge of the motor to the front edge of the plunger to the length from the rear edge of the shell to the front edge of the gun barrel interface is 0.2-0.35.

Further, the transmission mechanism comprises an eccentric shaft, the input end of the eccentric shaft is in transmission connection with the power output shaft of the motor, a groove for connecting the output end of the eccentric shaft is formed in the middle of the plunger, the output end of the eccentric shaft is at least partially contained in the groove and is in rotary connection with the plunger through a plunger bearing, and the plunger bearing adopts a needle bearing.

Further, the outer side wall of the needle bearing or the inner side wall of the groove is configured such that a gap between the needle bearing and the groove is larger than the middle in both ends in the axial direction.

Further, the transmission mechanism is a gear box, and the smaller size of the width and the height of the gear box is 50-55mm.

Further, the pump body has a dimension in the direction of extension of its plunger of 75-109.5mm.

Further, the high-pressure chamber comprises a first high-pressure chamber and a second high-pressure chamber which are correspondingly matched with the two ends of the plunger respectively; the transmission mechanism comprises an eccentric shaft, the input end of the eccentric shaft is in transmission connection with the power output shaft of the motor, the output end of the eccentric shaft is in rotary connection with the plunger, and the eccentric distance of the eccentric shaft is 3-6mm; the transmission mechanism converts the rotary motion of the motor into linear reciprocating motion of the plunger to enable the plunger to alternately compress or release the first high-pressure chamber and the second high-pressure chamber.

Further, the plunger of the pump body is arranged along the horizontal direction and is perpendicular to the axial direction of the power output shaft of the motor.

Further, the diameter of the plunger is 10-16mm, and the dimension of the pump body in the axial direction perpendicular to the extending direction of the plunger and perpendicular to the power output shaft of the motor is 40.5-68.5mm.

Further, the flow rate of the pump body is 180-300L/h.

Further, a water inlet valve is arranged on the water inlet channel, and the water inlet channel comprises a valve forward water inlet section and a valve rear water outlet section which are respectively arranged at two sides of the water inlet valve;

the water inlet valve comprises a valve core, a valve seat and a second elastic piece, wherein the valve core, the valve seat and the second elastic piece are radially arranged along a water inlet channel, the valve seat is provided with a cavity communicated with a valve advancing water section and a valve rear water outlet section, the valve core is arranged in the cavity in a guiding manner and is provided with a control end, the outer side wall of the valve core is provided with a sealing section and a water passing groove, the second elastic piece acts on the valve core to enable the valve core to automatically reset when no external force exists at the control end, the valve core is controlled to move relative to the valve seat through the control end, the valve advancing water section and the valve rear water outlet section are communicated through the water passing groove or sealed through the sealing section, and accordingly the water channel on-off between the valve advancing water section and the valve rear water outlet section is controlled.

Further, the water passing groove is of an up-down symmetrical structure along the extending direction of the valve core, so that the acting forces of water pressure on the upper side and the lower side of the water passing groove are equal in magnitude and opposite in direction.

The utility model has the following beneficial effects:

firstly, the motor is configured into the outer rotor brushless motor, so that the size is small, the weight is light, and the size and the weight of the handheld high-pressure cleaning machine can be greatly reduced; meanwhile, parameters such as the width and the height of the pump body, the diameter of the plunger, the eccentric wheelbase, the length of the motor, the size of the transmission mechanism and the like are reasonably set; on the premise of meeting the performance of the whole machine, the volume and the weight of the handheld high-pressure cleaning machine can be minimized; the device can effectively reduce the volume of the plunger pump when the pressure of the plunger pump is increased to more than 3Mpa and the flow is increased to 180-300L/h, realize the characteristics of high pressure, high flow, high efficiency, small volume, light weight and portability of the hand-held cleaning machine and improve the operation comfort level of the hand-held cleaning machine.

Secondly, the plunger bearing is a needle bearing, so that the diameter is small, the weight is light, and the machine is minimized and the weight is minimized on the premise of meeting the performance strength; in addition, the gap between the two ends of the matching surface between the needle roller bearing and the groove is larger than the middle part, so that the bearing end part is prevented from being damaged by stress, and the service life and the reliability of the product are improved.

Thirdly, the water inlet valve is arranged perpendicular to the water inlet direction, and the water flow is controlled to be on-off by radial sealing between the valve core and the valve seat, so that the acting force of water pressure on the axial direction of the valve core can be reduced; meanwhile, by arranging the water passing groove into an up-down symmetrical structure along the extending direction of the valve core, the water pressure is equal to the acting force on the upper side and the lower side of the water passing groove, and the acting forces are opposite in size and direction and offset each other, so that the water pressure has no resistance to the axial direction of the valve core when the valve core is pulled, and only the spring force and the friction force are overcome when the trigger is pressed to pull the valve core, the required operating force is smaller, the operation is more labor-saving, and the use comfort of a product can be improved.

Fourth, the utility model can reduce the size of the pump body in the extending direction of the plunger, and further can transversely arrange the plunger, so that the whole machine is bilaterally symmetrical, and the appearance is more coordinated and attractive.

Drawings

FIG. 1 is a cross-sectional view of a prior art single plunger pump having a pressure of 2.2MPa and a flow rate of 120L/h;

FIG. 2 is a top view of the single plunger pump of FIG. 1 with a pressure of 2.2MPa and a flow rate of 120L/h;

FIG. 3 is a cross-sectional view of a prior art single plunger pump having a pressure of 2.4MPa and a flow rate of 210L/h;

FIG. 4 is a top view of the single plunger pump of FIG. 3 with a pressure of 2.4MPa and a flow rate of 210L/h;

FIG. 5 is a cross-sectional view of a prior art single plunger pump having a pressure of 5MPa and a flow rate of 250L/h;

FIG. 6 is a top view of the single plunger pump of FIG. 5 with a pressure of 5MPa and a flow rate of 250L/h;

FIG. 7 is a cross-sectional view of a prior art three-plunger axial pump having a pressure of 3MPa and a flow rate of 250L/h;

FIG. 8 is a top view of the three plunger axial pump of FIG. 7 with a pressure of 3MPa and a flow rate of 250L/h;

FIG. 9 is a right side view showing the overall structure of a hand-held high-pressure washer according to the first embodiment of the present utility model;

fig. 10 is a cross-sectional view of the main body of the whole machine according to the first embodiment of the present utility model;

fig. 11 is a top structural cross-sectional view of a plunger pump according to a first embodiment of the present utility model;

fig. 12 is a bottom view of the plunger pump of the first embodiment of the present utility model;

FIG. 13 is a partial structural rear view of the plunger pump of the first embodiment of the present utility model, showing a rear view structure of the gear case;

fig. 14 is a perspective view showing the overall structure of a plunger pump according to a first embodiment of the present utility model;

fig. 15 is an exploded perspective view of a plunger pump according to a first embodiment of the present utility model;

fig. 16 is a front structural sectional view of a plunger pump according to a first embodiment of the present utility model;

FIG. 17 is a sectional view showing the mounting structure of the inlet valve on the inlet passage according to the first embodiment of the present utility model, showing an operating state when the waterway of the inlet passage is disconnected;

FIG. 18 is a sectional view showing an installation structure of a water inlet valve on a water inlet passage according to a first embodiment of the present utility model, showing an operation state when the water inlet passage is waterway-connected;

FIG. 19 is a cross-sectional view of the mounting structure of the transmission mechanism and motor and plunger connection of the first embodiment of the present utility model;

FIG. 20 is an exploded perspective view of the transmission mechanism of the first embodiment of the present utility model;

FIG. 21 is a partial sectional view of the plunger pump according to the first embodiment of the present utility model, showing the connection structure of the plunger and the eccentric shaft;

fig. 22 is a cross-sectional view of the needle bearing of the first embodiment of the present utility model;

fig. 23 is a left side view in cross section of the plunger pump of the first embodiment of the present utility model, showing the drain hole structure;

FIG. 24 is a left side view showing the overall structure of a hand-held cleaning machine according to a second embodiment of the present utility model;

fig. 25 is a top view of a plunger pump according to a second embodiment of the present utility model;

fig. 26 is a left side structural sectional view of a plunger pump according to a second embodiment of the present utility model;

fig. 27 is a perspective sectional view of a plunger pump according to a second embodiment of the present utility model;

FIG. 28 is a partial cross-sectional view of a plunger pump according to a third embodiment of the present utility model, showing the engagement of grooves of the plunger with needle bearings;

fig. 29 is a partial structural sectional view of the plunger pump of the fourth embodiment of the present utility model, showing the fitting structure of the grooves of the plunger and the needle bearings.

In the figure: 1. the hydraulic pump includes a barrel, 2, a housing, 21, a barrel port, 22, a handle, 23, a power supply portion, 24, a trigger, 3, a plunger pump, 31, a pump body, 311, a pump body, 312, a pump head, 313, a left pump cover, 314, a right pump cover, 315, a high pressure chamber, 3151, a first high pressure chamber, 3152, a second high pressure chamber, 316, a plunger, 3161, a recess, 3162, a first incline, 3163, a second incline, 3164, a third incline, 3165, an annular groove, 317, a water inlet passage, 3171, a water inlet, 3172, a water inlet check valve, 3173, a valve front inlet section, 3174, a valve rear water outlet section, 318, a water outlet, 3181, 3182, a water outlet check valve, 319, a plunger chamber, 3110, a water inlet pipe, 32, a motor, 321, a sun gear, 33, a transmission mechanism, 331, a planet carrier, 332, an eccentric shaft, 3321. Eccentric shaft input, 3322. Eccentric shaft output, 3323. Intermediate connection, 333. Bearing positioning bracket, 334. First bearing, 335. Second bearing, 336. Bearing, 3361. Curved surface, 337. Planetary gear, 338. Pin, 339. Sliding plate, 3301. First gear, 3302. Second gear, 341. Pressure relief channel, 342. Pressure relief device, 3421. Pressure relief valve plate, 3422. First spring, 35. Inlet valve, 351. Valve core, 3511. Control end, 3512. Sealing section, 3513. Water passing groove, 352. Valve seat, 353. Second spring, 354. Guide sleeve, 355. Plug, 361. First sealing member, 362. Second sealing member, 371. First guide sleeve, 372. Second guide sleeve, 381. Bearing cavity, 382. Drain hole.

Detailed Description

The following description of the embodiments of the present utility model will be made apparent and fully in view of the accompanying drawings, in which some, but not all embodiments of the utility model are shown. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.

In the description of the present utility model, it should be noted that the directions or positional relationships indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present utility model and simplifying the description, and do not indicate or imply that the mechanisms or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present utility model. 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 addition, the technical features of the different embodiments of the present utility model described below may be combined with each other as long as they do not collide with each other.

Referring to fig. 9 and 10, a hand-held high pressure cleaner according to a first embodiment of the present utility model includes a main body and a water outlet barrel 1. The whole machine main body comprises a shell 2 and a plunger pump 3, the plunger pump 3 comprises a pump body 31, a motor 32 and a transmission mechanism 33, the motor 32, the transmission mechanism 33 and the pump body 31 are arranged in the shell 2, and the motor 32 is connected with the pump body 31 through the transmission mechanism 33 and is used for driving the pump body 31 to operate.

Referring to fig. 10 and 11, the pump body 31 is a plunger pump body, and includes a high-pressure chamber 315, a plunger 316, a water inlet channel 317, and a water outlet channel 318. The high pressure chamber 315 includes a first high pressure chamber 3151 and a second high pressure chamber 3152 correspondingly and cooperatively disposed with both ends of the plunger 316. The plunger 316 is capable of reciprocating relative to the first and second high pressure chambers 3151, 3152 to pressurize the water flow. The water inlet channel 317 and the water outlet channel 318 are respectively communicated with the first high pressure chamber 3151 and the second high pressure chamber 3152. The water inlet 3171 is formed at the outer end of the water inlet channel 317, the water outlet 3181 is formed at the outer end of the water outlet channel 318, the water inlet 3171 is used for being connected with an external water source, and the water outlet 3181 is used for being connected with the water outlet barrel 1. The shell 2 is provided with a barrel joint 21 at the front end of a water outlet 3181 of the pump body 31 for connecting with the water outlet barrel 1, and the water outlet barrel 1 is connected with the barrel joint 21. The shell 2 and the water outlet gun barrel 1 form a handheld spray gun shell of a handheld high-pressure cleaning machine. The outer end of the water outlet gun barrel 1 is provided with a water flow nozzle. The water outlet channel 318 communicates with the water jet.

In this embodiment, the rated pressure output by the pump body 31 is 3-7Mpa, and the flow rate of the pump body is 180-300L/h. The product of the dimension of the motor 32 in the axial direction of the power output shaft thereof, the dimension of the pump body 31 in the extending direction of the plunger 316 thereof and the smaller dimension of the width and the height of the transmission mechanism is 190-230cm ³ . Wherein: the size of the motor 32 in its power take-off shaft axis is the primary dimension that affects the overall size of the motor; the dimension of the pump body 31 in the direction in which the plunger 316 extends affects the overall dimension of the pump bodyIs a major dimension of (2); the transmission mechanism 33 is a gear box, the gear box comprises a speed reducer, the smaller size of the width and the height of the gear box corresponds to the diameter size of the disk structure of the gear box, and the size is the main dimension for determining the whole size of the gear box due to flexible design of surrounding mounting structures; the three dimensions determine the overall dimensions of the motor 32, the pump body 31 and the gear box, respectively, and together affect the overall dimensions of the plunger pump 3, so that the product of the three dimensions is small, which also results in a small volume of the plunger pump 3. At least 70% of the cross-section of the pump body 31 taken in a plane passing through the plunger 316 and perpendicular to the axial direction of the power output shaft of the motor (i.e., the plane formed by the direction b and the direction c in fig. 9 to 12) has an area of 33.6-59.6cm ² . Referring to fig. 11 to 13, the motor 32 is an external rotor brushless motor, the rotation speed of the motor 32 is 10000r/min-30000r/min, and the length L3 of the motor 32 in the axial direction of the power output shaft thereof (i.e., in the direction shown in a of fig. 11 and 12) is 42-55mm; the plunger 316 of the pump body 31 is arranged along the horizontal direction and is perpendicular to the axial direction of the power output shaft of the motor 32, the dimension of the pump body 31 in the extending direction of the plunger 316 (i.e. in the direction b shown in fig. 11 and 12) corresponds to the width of the pump body 31, the width of the pump body 31 is larger than the height of the pump body 31, the width W of the pump body is 75-109.5mm, the height H of the pump body is 40.5-68.5mm, and the height of the pump body is the dimension of the pump body in the direction c shown in fig. 9 and 13; the gearbox has a height less than the width, a gearbox height E of 50-55mm, and a gearbox height dimension in the direction indicated by c in fig. 9 and 13.

Referring to fig. 9 and 11, the whole machine body is configured to: in the axial direction of the power output shaft of the motor 32 (i.e., in the direction shown in fig. 9 and 11 a), the ratio of the length L1 from the rear edge of the motor 32 to the front edge of the plunger 316 to the length L2 from the rear edge of the housing 2 to the front edge of the barrel port 21 is 0.2-0.35; wherein: the length L1 from the trailing edge of the motor 32 to the leading edge of the plunger 316 is 95-110mm and the length L2 from the trailing edge of the housing 2 to the leading edge of the barrel port 21 is 320-340mm.

Preferably, in the embodiment, the rated pressure output by the pump body 31 is 3-6MPa, the flow is 180-220L/h, the length L3 of the motor 32 is 42-50mm, the width W of the pump body 31 is 75-80mm, and the height E of the gear box is 50-55mm. In the axial direction of the power output shaft of the motor 32, the length L1 from the rear edge of the motor 32 to the front edge of the plunger 316 is 95-105mm, the length L2 from the rear edge of the shell 2 to the front edge of the gun barrel interface 21 is 325-335mm, and the length L4 of the integral main body connected with the water gun barrel 1 is 800-900mm.

Referring to fig. 11, the transmission mechanism 33 includes an eccentric shaft 332, a groove 3161 for connecting the eccentric shaft 332 is formed in the middle of the plunger 316, and the depth of the groove 3161 is not less than 1/2 of the diameter of the plunger. The eccentric shaft input end 3321 is in transmission connection with the power output shaft of the motor 32, and the eccentric shaft output end 3322 is at least partially accommodated in the groove 3161 and is in rotary connection with the plunger 316 through a plunger bearing 336. The transmission 33 converts the rotational motion of the motor 32 into linear reciprocating motion of the plunger 316.

In this embodiment, the diameter of the plunger 316 is 10-16mm, and the eccentricity of the eccentric shaft 332 is 3-6mm.

Specifically, in this embodiment, the diameter of the plunger 316 is 10-14mm, the eccentricity of the eccentric shaft 332 is 3-4.5mm, and the stroke of the plunger 316 is 7-8mm; the rotation speed of the motor 32 is 15000-20000r/min, the transmission ratio is 7-8, and the volumetric efficiency is 80-90%.

Referring to fig. 11, 14 and 15, the pump body 31 further includes a pump body 311, a pump head 312, a left pump cover 313, a right pump cover 314 and a water inlet pipe 3110, the pump body 311 is respectively connected with the pump head 312, the left pump cover 313 and the right pump cover 314, the first high-pressure chamber 3151 and the second high-pressure chamber 3152 are formed between the pump body 311 and the left pump cover 313, between the right pump cover 314 and the plunger 316, the water outlet channel 318 is formed between the pump body 311 and the pump head 312, the water inlet channel 317 is formed between the pump body 311 and the water inlet pipe 3110, and the plunger cavity 319 for accommodating the plunger 316 is also formed in the pump body 311.

The first high-pressure chamber 3151 and the second high-pressure chamber 3152 are respectively provided with a high-pressure chamber water inlet and a high-pressure chamber water outlet, the water inlet channel 317 is respectively communicated with the high-pressure chamber water inlets of the first high-pressure chamber 3151 and the second high-pressure chamber 3152 through the water inlet check valve 3172, and the water outlet channel 318 is respectively communicated with the first high-pressure chamber 3151 and the second high-pressure chamber through the water outlet check valve 3182The high pressure chamber outlet of chamber 3152 communicates. The inlet check valve 3172 can be opened and closed as the water pressure in the high pressure chamber 315 decreases. The outlet check valve 3182 can be closed and opened as the water pressure in the high pressure chamber 315 decreases. In the existing cleaning machine, the cross section area of a flow passage between a water inlet one-way valve and a water inlet of a high-pressure chamber is 19mm ² The area is smaller, and the speed of liquid water entering the high-pressure chamber through the water inlet one-way valve is limited. In this embodiment, preferably, the cross-sectional area of the flow path between the water inlet check valve 3172 and the water inlet of the high pressure chamber is not less than 35mm ² The water inflow rate can be improved. The specific structure and installation manner of the water inlet check valve 3172 and the water outlet check valve 3182 are the prior art, and are not described herein. The water inlet check valve 3172 and the water outlet check valve 3182 may be formed by a section of spring and a valve body connected to an end of the spring, but are not limited thereto.

Referring to fig. 11, the plunger 316 reciprocates between a first position, which is an extreme position at which the plunger 316 moves toward the first high-pressure chamber 3151, and a second position, which is an extreme position at which the plunger 316 moves toward the second high-pressure chamber 3152. When the plunger 316 moves from the first position to the second position, the volume of the first high-pressure chamber 3151 gradually increases, the water pressure decreases, at this time, the water inlet check valve 3172 corresponding to the first high-pressure chamber 3151 is opened, the water outlet check valve 3182 is closed, and the liquid water flows into the first high-pressure chamber 3151 from the water inlet channel 317; meanwhile, the volume of the second high pressure chamber 3152 gradually decreases to pressurize the liquid water in the second high pressure chamber 3152, at this time, the water inlet check valve 3172 corresponding to the second high pressure chamber 3152 is closed, the water outlet check valve 3182 is opened, and the liquid water flows out from the second high pressure chamber 3152 to the water outlet channel 318. Conversely, when the plunger 316 moves from the second position to the first position, liquid water flows out from the first high-pressure chamber 3151 to the water outlet passage 318, and flows into the second high-pressure chamber 3152 from the water inlet passage 317; and so forth. The plunger 316 alternately compresses or releases the first high-pressure chamber 3151 and the second high-pressure chamber 3152, and water sequentially passes through the water inlet channel 317, the first high-pressure chamber 3151 or the second high-pressure chamber 3152 and the water outlet channel 318 to finally form high-pressure water flow, and the high-pressure water flow is sprayed out by the water outlet barrel 1 of the hand-held cleaning machine for cleaning operation.

In the existing cleaning machine, a pressure relief device which is communicated with a water inlet channel and a water outlet channel is arranged and used for relieving pressure when the pressure in the water outlet channel is overlarge, so that the safety performance of the plunger pump is improved, and the pressure relief device is at least partially positioned in the water inlet channel to form water inlet resistance, so that the high flow requirement of the plunger pump is not met. In order to obtain a plunger pump with small volume and large flow, in this embodiment, referring to fig. 16, a pressure relief channel 341 for communicating the water inlet channel 317 and the water outlet channel 318 is arranged between the water inlet channel 317 and the water outlet channel 318, the pressure relief channel 341 and the water inlet channel 317 are respectively arranged independently and are distributed in parallel side by side, and a pressure relief device 342 is arranged in the pressure relief channel 341. The space occupying the water inlet channel can be avoided, the flow rate of the water inlet channel 317 is enlarged, and the pressure relief device 341 and the water inlet channel 317 are arranged in parallel, so that the volume can be reduced on the premise of not affecting the performance of the plunger pump 3. The pressure relief device 342 includes a pressure relief valve plate 3421 and a first elastic member 3422 connected to and acting on the pressure relief valve plate 3421, and the pressure of the water outlet channel 318 acts on the pressure relief device 342 to switch the pressure relief valve plate 3421 between a state of closing and opening the pressure relief channel 341. The first elastic member 3422 employs a spring. However, the structures of the pressure release device 342 and the first elastic member 3422 are not limited thereto.

Referring to fig. 17 and 18, the water inlet valve 35 is disposed on the water inlet channel 317, and the water inlet channel 317 includes a valve front water inlet section 3173 and a valve rear water outlet section 3174 respectively disposed at two sides of the water inlet valve 35; the inlet valve 35 comprises a valve core 351, a valve seat 352, a second elastic member 353, a guide sleeve 354 and a bolt 355 which are arranged along the radial direction of the water inlet channel 317, wherein the valve seat 352 is provided with a cavity communicated with the valve advancing water section 3173 and the valve rear water outlet section 3174, the valve core 351 is arranged in the cavity in a guiding way and is provided with a control end 3511, and the control end 3511 is connected and linked with the trigger 24 of the hand-held high-pressure cleaner. The outer side wall of the valve core 351 is formed with a sealing section 3512 and a water passing groove 3513, the second elastic member 353 acts on the valve core 351 to enable the valve core 351 to reset automatically when no external force is applied to the control end 3511, the valve core 351 is controlled to move relative to the valve seat 352 through the control end 3511, the valve inlet section 3173 and the valve outlet section 3174 are communicated through the water passing groove 3513 or sealed through the sealing section 3512, and accordingly the water path between the valve inlet section 3173 and the valve outlet section 3174 is controlled to be opened or closed. The water passing tank 3513 has a vertically symmetrical structure along the extending direction of the valve core 351, so that the forces of water pressure on the upper side and the lower side of the water passing tank 3513 are equal and opposite. The guide sleeve 354 is arranged in the cavity of the valve seat 352, the outer side is limited by the bolt 355 to prevent the valve core 351 and the second elastic piece 353 from falling out, and the valve core 351 and the second elastic piece 353 are movably arranged in the guide sleeve 354 in a guiding way, so that the movement of the valve core 351 is guided. The second elastic member 353 employs a spring. As shown in fig. 17, when the valve core 351 is at the initial position, the water pressure is equal to the upper and lower acting forces of the water tank 3513 of the valve core 351, and the forces are opposite in direction and offset each other, so that the water pressure has no resistance to the axial direction of the valve core 351 when the valve core 351 is pulled; as shown in fig. 18, when the valve core 351 is opened, the flow passage is opened, the water pressure is still not resistant to the axial direction of the valve core 351, at this time, the trigger 24 is released, and the valve core 351 is restored to the original position under the spring force of the second elastic member 353. When the trigger 24 is pressed to pull the valve core 351 in the process, only the spring force and the friction force are overcome, and the hydraulic pressure is not blocked, so that the operation is more labor-saving, and the use comfort of the product can be improved. In addition, the inlet valve 35 configuration may be adapted for any gun closing linkage, and is not limited to trigger 24.

Referring to fig. 11, a first sealing member 361 and a second sealing member 362 are disposed in the plunger cavity 319, the first sealing member 361 and the plunger 316 form a first sealing structure, liquid water in the first high-pressure chamber 3151 is prevented from entering a space where the transmission mechanism 33 is located, the second sealing member 362 and the plunger 316 form a second sealing structure, liquid water in the second high-pressure chamber 3152 is prevented from entering a space where the transmission mechanism 33 is located, parts in the transmission mechanism 33 are prevented from rusting when meeting water, and the service life of the plunger pump 3 is prolonged. The first seal 361 and the second seal 362 may have a seal ring or the like.

Referring to fig. 11, a first guide sleeve 371 is formed on the inner wall of the plunger cavity 319 near the first high-pressure chamber 3151, a second guide sleeve 372 is formed on the inner wall near the second high-pressure chamber 3152, the plunger 316 is arranged between the first guide sleeve 371 and the second guide sleeve 372 in a guiding manner, the first guide sleeve 371 and the second guide sleeve 372 are used for guiding the plunger 316 to move between the first position and the second position, accuracy of movement of the plunger 316 is improved, and abrasion during reciprocating movement of the plunger 316 can be reduced. The existing plunger pump has the problems that the installation position of the guide sleeve is too close to the middle of the plunger, the distance between the guide sleeve and the top end of the plunger is too large, the abrasion of the plunger is not reduced, and the guide precision is insufficient. In this embodiment, the first guide sleeve 371 is disposed near the first high pressure chamber 3151, and the second guide sleeve 372 is disposed near the second high pressure chamber 3152, so that the guide accuracy can be improved and the abrasion of the plunger 316 can be reduced.

When the plunger pump 3 works, the motor 32 drives the plunger 316 to reciprocate through the eccentric shaft 332 to pressurize liquid water in the first high-pressure chamber 3151 or the second high-pressure chamber 3152 at two ends of the plunger 316, the reaction force of water pressure in the reciprocation process causes the plunger bearing 336 between the eccentric shaft 332 and the plunger 316 to bear large dynamic load, the larger the pressure is, the larger the reaction force of water pressure is, the larger the bearing force born by the plunger bearing 336 is, and if the plunger bearing 336 is a ball bearing, the larger diameter ball bearing is required to be selected in order to realize the pressure of 3-7MPa, the dynamic load of the plunger bearing 336 is required to be more than 4-7 KN. The needle roller bearing is provided with a thin and long roller (the length of the roller is 3-10 times of the diameter, and the diameter is generally not more than 5 mm), so that the radial structure is compact, and the outer diameter is the smallest when the inner diameter size and the load capacity are the same as those of other types of bearings. In order to reduce the volume of the plunger pump 3, in this embodiment, as shown in fig. 21 and 22, the plunger bearing 336 is a needle bearing, which is beneficial to reduce the length of the plunger 316. The needle bearing is used for realizing the equivalent pressure of 3-7MPa, the volume of the pump body 31 is 40-50% smaller than that of the pump body using the ball bearing, and the effect of small volume and high load is achieved. In addition, when the mating surface between the plunger 316 and the eccentric shaft output end 3322 is a regular plane, the perpendicularity of the pump body 31 is poor due to machining tolerance and assembly error of the pump body 31 and pump body abrasion in the long-term use process, so that the needle roller bearing between the plunger 316 and the eccentric shaft output end 3322 is easy to be stressed unevenly, the tip of the needle roller bearing is stressed, the retainer of the needle roller bearing is easy to be stressed and damaged, the needle roller bearing is damaged, and the service life of the plunger pump 3 is shortened. To solve this problem, in this embodiment, the outer side wall of the needle bearing is configured such that the gap between the needle bearing and the groove 3161 is larger than the curved surface 3361 in the middle at both ends in the axial direction, ensuring that the mating surface of the needle bearing and the plunger 316 is stressed centrally, and avoiding the wear of the tip of the needle bearing. In addition, a sliding plate 339 is arranged between the needle bearing and the second bearing 335, so that friction of the end face between the needle bearing and the second bearing 335 can be reduced, damage of the needle bearing caused by friction is reduced, and service life of the needle bearing is prolonged.

Referring to fig. 23, the pump body 31 is formed with a bearing chamber 381 for accommodating the plunger bearing 336, and the pump body 31 is provided with a drain hole 382 communicating the inside of the bearing chamber 381 with the outside of the pump body 31 at the bearing chamber 381. In this embodiment, the plunger 316 is laterally disposed, the drain hole 382 is disposed at the bottom of the housing 2, and the drain hole 382 is disposed perpendicular to the plunger 316.

Referring to fig. 19 and 20, the transmission mechanism 33 adopts a planetary gear transmission structure, and includes a planetary carrier 331, a planetary gear set, an eccentric shaft 332, a bearing and a bearing positioning carrier 333. The eccentric shaft 332 includes an eccentric shaft input end 3321, an eccentric shaft output end 3322, and an intermediate connection portion 3323 connected between the eccentric shaft input end 3321 and the eccentric shaft output end 3322 and coaxially disposed with the eccentric shaft input end 3321, wherein a first bearing 334, a second bearing 335 and a plunger bearing 336 are correspondingly disposed outside the eccentric shaft input end 3321, the intermediate connection portion 3323 and the eccentric shaft output end 3322, respectively, so as to position the eccentric shaft 332 in the pump body 31 relatively stably, and vibration is not easy to generate during rotation, noise is reduced, and stability is improved. The first bearing 334 and the second bearing 335 are mounted on the bearing positioning bracket 333, and the planetary gear set includes three sequentially engaged planetary gears 337, and the three planetary gears 337 are rotatably mounted on the planetary bracket 331 through a pin 338. The planet carrier 331, the pin 338, the eccentric shaft 332, the first bearing 334, the second bearing 335, the plunger bearing 336 and the bearing positioning carrier 333 are connected by interference fit. Parts can be processed independently, so that the processing technology of parts such as a transmission shaft, a planet carrier and the like is simplified remarkably, and the overall cost can be reduced effectively. The outer end of the power output shaft of the motor 32 is fixedly sleeved with a sun gear 321, the sun gear 321 is in meshed transmission connection with a first-stage planetary gear 337 in the planetary gear set, and the input end of an eccentric shaft is in synchronous rotation connection with a third-stage planetary gear 337.

The pump body 31 comprises a pump housing, and is formed by connecting the pump body 311, a pump head 312, a left pump cover 313, a right pump cover 314 and a water inlet pipe 3110; the transmission mechanism comprises a transmission supporting mechanism, and comprises the planet carrier 331 and a bearing positioning carrier 333; the pump housing of the pump body 31 and the transmission supporting mechanism of the transmission mechanism 33 are made of plastic materials, so that the machine is minimum, the weight is minimum and the cost is minimum on the premise of meeting the product performance and the service life. Preferably, the bare metal weight (excluding the battery pack) does not exceed 2.2Kg.

Referring to fig. 9 and 10, the main body further includes a handle 22 formed on the housing 2 for holding, a switch rotatably mounted on the housing 2 for opening and closing the hand-held high-pressure cleaner, and a power supply 23 disposed on the housing 2 for supplying power. The handle 22 is located at the rear side of the housing 2, the power supply portion 23 is disposed at the front side of the handle 22, the power supply portion 23 is electrically connected with the motor 32 of the plunger pump 3, a contact switch (not shown) for controlling the motor to start or stop is further disposed between the power supply portion 23 and the motor 32, and a cable (not shown) for at least partially realizing the electrical connection is disposed inside the handle 22. The power supply unit 23 may be a battery pack or a power cord for connecting to the commercial power. The switch is provided between the handle 22 and the power supply unit 23, and is linked to the valve body 351 of the water inlet valve 35. Preferably, in this embodiment, the power supply portion 23 is a battery pack, and the switch member is a trigger 24. By arranging the power supply part 23 and the switch element near the handle 22, wiring is facilitated, and the whole structure of the hand-held high-pressure cleaner is more compact.

Referring to fig. 24 to 27, the hand-held high pressure washer of the second embodiment of the present utility model is different from the first embodiment in that:

the water inlet valve 35 is not provided on the water inlet channel 317 of this embodiment.

Referring to fig. 26, the transmission mechanism 33 is an external engagement transmission structure. The eccentric shaft input end 3321 and the power output shaft of the motor 32 are arranged in parallel and are positioned on different axes, and the eccentric shaft input end 3321 and the power output shaft of the motor 32 are provided with mutual interference sections in the axial direction so as to realize transmission connection of the eccentric shaft input end 3321 and the power output shaft of the motor 32 through transmission assemblies arranged on radial planes, thereby saving axial space. The transmission assembly may include a first gear 3301 and a second gear 3302 meshed with each other, where the first gear 3301 is fixedly sleeved on a power output shaft of the motor 32, the second gear 3302 is fixedly sleeved on an input end 3321 of the eccentric shaft, the motor 32 is started, and the power output shaft of the motor 32 drives the first gear 3301 to rotate synchronously, so as to drive the second gear 3302 and the eccentric shaft 332 to rotate. The transmission assembly structure is not limited thereto, and other gears may be provided between the first gear 3301 and the second gear 3302, and inner engagement may be provided between the first gear 3301 and the second gear 3302.

The pump body 31 is longitudinally arranged, that is, the plunger 316 is longitudinally arranged, the drain holes 382 are formed on two sides of the housing 2, and the drain holes 382 are perpendicular to the plunger.

Referring to fig. 24, the power supply unit 23 is connected to the lower side of the handle 22.

In the present embodiment, preferably, the rated pressure of the pump body 31 is 3-6MPa, the pump body flow rate is 200-250L/h, and more than 70% of the cross section of the pump body 31 cut by the plane passing through the plunger 316 and perpendicular to the axial direction of the power output shaft of the motor 32 has an area of 33.6-59.6cm ² (because the outer edge of the pump body may have uneven conditions or some ribs or grooves for fixing are arranged on the surface of the pump body, the height H of the pump body and the width W of the pump body are not fixed values, and the cross-sectional area of the pump body is affected); the height H of the pump body 31 is 79.2-98.5mm, and the width W is 40.5-60.5mm; the eccentric distance of the eccentric shaft 332 is 3.1-3.5mm; the travel of the plunger 316 is 6.2-7.0mm.

Referring to fig. 28, the hand-held high pressure washer of the third embodiment of the present utility model is different from the first embodiment in that: in order to ensure that the matching surface of the needle bearing and the plunger 316 is stressed in the middle, so as to avoid the wear of the tip of the needle bearing, in this embodiment, the two ends of the inner side wall of the plunger groove 3161 in the axial direction are respectively chamfered, so that the two ends of the needle bearing are not contacted with the inner side wall of the plunger groove 3161, and the tip of the needle bearing is prevented from being stressed. Specifically, a first inclined surface 3162 is formed at an opening end of the plunger recess 3161, and a second inclined surface 3163 is formed at a distance from the opening end.

Referring to fig. 29, the hand-held high pressure washer of the fourth embodiment of the present utility model is different from the first embodiment in that: in order to ensure that the matching surface of the needle bearing and the plunger 316 is stressed in the middle, so as to avoid the wear of the tip of the needle bearing, in this embodiment, the outer end chamfer and the inner end of the inner side wall of the plunger groove 3161 in the axial direction are grooved, so that the two ends of the needle bearing are not contacted with the inner side wall of the plunger groove 3161, and the stress of the tip of the needle bearing is avoided. Specifically, a third inclined surface 3164 is formed at an open end of the plunger recess 3161, and an annular groove 3165 is formed at a distal end from the opening.

The technical features of the above embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.

The foregoing examples illustrate only a few embodiments of the utility model, which are described in detail and are not to be construed as limiting the scope of the utility model. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the utility model, which are all within the scope of the utility model. Accordingly, the scope of protection of the present utility model is to be determined by the appended claims.

Claims (13)

1. The handheld high-pressure cleaning machine is characterized by comprising a handheld spray gun shell, a pump body, a transmission mechanism and a motor, wherein the pump body, the transmission mechanism and the motor are arranged in the handheld spray gun shell;

the handheld spray gun shell is provided with a water flow nozzle;

the pump body comprises a high-pressure chamber, a plunger, a water inlet channel and a water outlet channel, the plunger can do reciprocating motion relative to the high-pressure chamber so as to pressurize water flow, the water inlet channel and the water outlet channel are respectively communicated with the high-pressure chamber, and the water outlet channel is communicated with the water flow nozzle;

the transmission mechanism comprises a speed reducer, and the motor is connected with the speed reducer and drives the plunger to reciprocate relative to the high-pressure chamber;

the motor is configured as an outer rotor brushless motor, the size of the motor in the axial direction of a power output shaft of the motor is 42-55mm, and the size of the motor from the rear edge of the motor to the front edge of a plunger in the axial direction of the power output shaft of the motor is 95-110 mm.

2. The hand-held high-pressure washer according to claim 1, wherein the pump body output end rated pressure is 3-7MPa, the product of the size of the motor in the axial direction of the power output shaft thereof, the size of the pump body in the extending direction of the plunger thereof, and the smaller size of the width and the height of the transmission mechanism is 190-230cm ³ 。

3. The hand-held high pressure washer of claim 1 or 2, wherein the hand-held spray gun housing comprises a housing and a water outlet barrel, the motor, transmission mechanism and pump body being mounted in the housing;

the shell is provided with a gun barrel interface for connecting the water outlet gun barrel at the front end of the water outlet channel of the pump body;

in the axial direction of the power output shaft of the motor, the ratio of the length from the rear edge of the motor to the front edge of the plunger to the length from the rear edge of the shell to the front edge of the gun barrel interface is 0.2-0.35.

4. The hand-held high-pressure cleaning machine according to claim 1 or 2, wherein the transmission mechanism comprises an eccentric shaft, the input end of the eccentric shaft is in transmission connection with the power output shaft of the motor, a groove for connecting the output end of the eccentric shaft is formed in the middle of the plunger, and the output end of the eccentric shaft is at least partially accommodated in the groove and is in rotary connection with the plunger through a plunger bearing, and the plunger bearing adopts a needle bearing.

5. The hand-held high pressure washer of claim 4, wherein the needle bearing outer sidewall or the groove inner sidewall is configured such that a gap between the needle bearing and the groove is larger at both ends than at the middle in an axial direction.

6. A hand-held high pressure washer according to claim 1 or 2, wherein the transmission is a gearbox, the smaller of the width and height of which is 50-55mm.

7. A hand-held high pressure washer according to claim 1 or 2, wherein the pump body has a dimension in the direction of extension of its plunger of 75-109.5mm.

8. The hand-held high pressure washer of claim 7, wherein the high pressure chamber comprises a first high pressure chamber and a second high pressure chamber correspondingly and cooperatively disposed with each of the two ends of the plunger; the transmission mechanism comprises an eccentric shaft, the input end of the eccentric shaft is in transmission connection with the power output shaft of the motor, the output end of the eccentric shaft is in rotary connection with the plunger, and the eccentric distance of the eccentric shaft is 3-6mm; the transmission mechanism converts the rotary motion of the motor into linear reciprocating motion of the plunger to enable the plunger to alternately compress or release the first high-pressure chamber and the second high-pressure chamber.

9. The hand-held high pressure washer of claim 7, wherein the plunger of the pump body is disposed in a horizontal direction and is axially perpendicular to the power take-off shaft of the motor.

10. A hand-held high pressure cleaner according to claim 1 or 2, wherein the plunger has a diameter of 10-16mm and the pump body has a dimension of 40.5-68.5mm in an axial direction perpendicular to the direction in which the plunger extends and perpendicular to the motor power take-off shaft.

11. The hand-held high-pressure washer according to claim 1 or 2, wherein the pump body has a flow rate of 180-300L/h.

12. The hand-held high-pressure washer according to claim 1 or 2, wherein the water inlet channel is provided with a water inlet valve, and the water inlet channel comprises a valve forward water section and a valve rear water outlet section which are respectively arranged at two sides of the water inlet valve;

the water inlet valve comprises a valve core, a valve seat and a second elastic piece, wherein the valve core, the valve seat and the second elastic piece are radially arranged along a water inlet channel, the valve seat is provided with a cavity communicated with a valve advancing water section and a valve rear water outlet section, the valve core is arranged in the cavity in a guiding manner and is provided with a control end, the outer side wall of the valve core is provided with a sealing section and a water passing groove, the second elastic piece acts on the valve core to enable the valve core to automatically reset when no external force exists at the control end, the valve core is controlled to move relative to the valve seat through the control end, the valve advancing water section and the valve rear water outlet section are communicated through the water passing groove or sealed through the sealing section, and accordingly the water channel on-off between the valve advancing water section and the valve rear water outlet section is controlled.

13. The hand-held high pressure washer of claim 12, wherein the water passing trough has a vertically symmetrical structure along the extending direction of the valve core, so that the forces of water pressure on the upper and lower sides of the water passing trough are equal and opposite.

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