CN215212921U - Hydraulic hinge mandrel capable of adjusting oil return speed - Google Patents

Abstract

The utility model provides a hydraulic pressure hinge dabber of adjustable return oil speed, it includes main part pipe, the needle, the oil return needle, the cylinder body, a piston, main spring and connection main shaft, the closed cavity between piston and the cylinder body forms the oil storage chamber, the piston can be under the effect of the inside and outside pressure differential of oil storage chamber axial displacement, the check valve on the piston forms the oil feed passageway, there is the speed governing valve hole in the piston center, the one end of oil return needle is connected on the cylinder body, the other end inserts in the speed governing valve hole, the needle cover is outside the oil return needle, the cylinder body lateral wall has been seted up the pressure release hole, the needle blocks up the pressure release hole, the oil pressure is too big, the needle shifts up, the passageway that the pressure release hole belongs to forms first draining passageway; the oil return needle comprises a thin part in the middle and thick parts at two ends, the thick parts are variable in diameter, and a second oil drainage channel is formed by a gap between the oil return needle and the speed regulation valve hole. The height position of the oil return needle in the mandrel is adjusted, the closing angle of the mandrel in the inertia force stage is adjusted when the mandrel is closed, and the door closing speed is adjusted. The size of the oil passing amount of the speed regulating valve hole is adjusted, and the buffering is provided when the door is opened and closed.

Description

Hydraulic hinge mandrel capable of adjusting oil return speed

Technical Field

The utility model relates to a hydraulic pressure technical field, concretely relates to hydraulic pressure hinge dabber of adjustable oil return speed.

Background

In the hinge field, the hydraulic buffer hinge is popular due to the unique functionality, the hydraulic buffer hinge realizes automatic door closing through the resilience force of a spring, and controls the door closing speed through the buffer action of hydraulic damping so as to prevent abrasion and noise caused by strong impact between a door and a door frame when the door is closed.

The invention patent with the application number of CN20190874254.9 discloses a mandrel and an anti-violence universal hydraulic hinge with the mandrel, when a door is closed, a main spring compresses tightly to apply an upward force to a piston, the piston applies pressure to oil in a cylinder body, the pressure is transmitted to a valve needle, an oil supply valve pressure spring applies upward pressure to jack the valve needle, hydraulic oil flows back to a hydraulic oil bin from a pressure relief oil way to realize buffering, and the hydraulic effect is fast and slow. Finally, the piston reaches a certain point in the cylinder body to be contacted with the valve needle, the valve needle is completely ejected, pressure is instantly discharged, and the valve is locked. The patent is not enough in that the door closing process has three stages, the valve needle is jacked up by depending on oil pressure, the buffering and the valve needle jacking by the piston are realized by the pressure relief oil path, and the three stages have different door closing speeds. The speed of the first stage is influenced by the external force of closing the door, and the buffering is not opened because the pressure relief oil path is not opened. In the second and third phases, the flow of hydraulic oil hinders the spring from closing the door quickly, i.e. damping. However, the speed of the second and third phases of closing is not adjustable, which results in an unstable closing process.

SUMMERY OF THE UTILITY MODEL

In order to solve the problem, the utility model provides a hydraulic hinge dabber of adjustable oil return speed, slow and the speed of closing the door is stable, and can regulate and control the speed of closing the door.

A hydraulic hinge mandrel capable of adjusting oil return speed comprises a main body pipe, a cylinder body, a piston, a lower cam ring, a main spring, a connecting main shaft and a pressure positioning sleeve, wherein the upper cam ring, the piston, the lower cam ring, the main spring, the connecting main shaft and the pressure positioning sleeve are sequentially arranged in the main body pipe from top to bottom; the top of the cylinder body is provided with an adjusting screw position, the adjusting screw position is communicated with the oil storage cavity through a conical valve hole, and the side wall of the conical valve hole is provided with a pressure relief hole; the hydraulic hinge mandrel further comprises a valve needle assembly, the valve needle assembly comprises a main screw, a spring, a valve needle, a C-shaped clamp spring, an adjusting screw and an oil return needle, the main screw is installed in the adjusting screw, the center of the main screw is an accommodating hole, the adjusting screw is installed in the accommodating hole, the oil return needle is connected to the lower portion of the adjusting screw, the spring is sleeved on the outer wall of the accommodating hole, the valve needle is installed below the spring in a clamping mode through the C-shaped clamp spring, the valve needle is used for blocking a pressure release hole, when the pressure in an oil storage cavity is too high, the valve needle moves upwards, and the pressure release hole forms a first oil drainage channel; the oil return needle comprises a thin part in the middle and thick parts at two ends, the thick parts are variable in diameter, and a second oil drainage channel is formed in a gap between the oil return needle and the speed regulation valve hole.

The utility model discloses a theory of operation does: during the door opening process, the door is manually opened, the connecting main shaft rotates, the piston rotates under the driving of the connecting main shaft and moves to one end close to the main spring, the speed regulation valve hole is not completely blocked by the thick part below the thin part, and the second oil drainage channel is limited in flow. The main spring is compressed due to the movement of the piston, the space of the oil storage cavity expands, the oil pressure is reduced, and the hydraulic oil in the hydraulic oil bin flows back into the oil storage cavity through the one-way valve of the piston. Normally close the door in-process, the door self-closing under the resilience force effect of main spring, the main spring resets gradually, the piston rotates on one side and removes to the one end that is close to the oil return needle under the drive of connecting the main shaft, oil storage chamber space is compressed, the oil pressure increase, the piston removes makes the oil return needle be in the speed governing valve hole, the hydraulic oil of oil storage chamber passes through the speed governing valve hole and discharges oil to hydraulic oil storehouse through the main oil route, oil needle thin part is the quick oil level of discharging, thick portion reducing is the position of leaking slowly. The door is slowly closed to achieve the buffer effect. In-process is closed to violence, the main spring compresses tightly and applies an ascending power for the piston, and the piston exerts pressure to the oil of oil storage intracavity, and pressure transmission gives the needle, and then the produced oil storage intracavity pressure of violence is too big and lead to the needle to move up, and first draining passageway is opened, and hydraulic oil flows back to the oil storage chamber outside from the first draining passageway at pressure release hole place, realizes the buffering, and hydraulic pressure effect is by fast and slow. Along with the attenuation of violence and the outflow of hydraulic oil, the pressure release hole is blockked up in the decline of valve needle, and first draining passageway closes. The hydraulic oil rethread second draining passageway in the surplus oil storage intracavity flows, and the hydraulic oil in oil storage chamber is passed through the second draining passageway and is leaked oil to hydraulic pressure oil bunker, and the axial motion of piston slows down, makes the door slowly close, reaches the cushioning effect. In conclusion, under the normal door closing state, only through oil return needle draining, when meeting the violence and closing the door, the needle can be jack-up, follows the pressure release hole draining, then follows oil return needle draining again. The oil return needle is fixed, but can move up and down to adjust the height position of the oil return needle in the mandrel, the fine part of the oil return needle is the rapid oil discharge level, the length of the rapid oil discharge level is changed by adjusting the height position of the oil return needle in the mandrel, the closing angle of the mandrel in the inertia force stage is adjusted when the mandrel is closed, and the adjustment of the door closing speed is realized. The utility model discloses a two kinds of modes can be adjusted into to the dabber, and these two kinds of modes are the silence mode respectively and lock the mode. The thick part is a hydraulic buffer position, and the thin part is an instant discharge position. The detailed function is that quick oil discharge is equivalent to no hydraulic buffer. The rear section door closing angle is favorable for inertial locking, which is called a locking function. The lower end position of the thin part is really completely discharged when passing through the position of the speed regulating valve hole. The details are completely adjusted, and basically, the thick part is called a full-section closing hydraulic buffering mode. The silent mode is basically a full line bold. For example, setting a certain height position of the oil return needle in the mandrel has the effect that when the door is closed, the door reaches the position of about 25-30 degrees of the door frame, and the thin part is positioned in the speed regulating valve hole to quickly discharge oil to form inertia force locking. The range of 25 ° to 30 ° is a value that can be configured to a desired inertial door closing angle, for example, 10 or 15 °, if the setting is full-buffer, i.e., the silent mode described above. Use the utility model discloses a dabber even meet the condition that the violence was closed the door, the atress is great when beginning promptly, leads to the too big condition of oil pressure, and the needle feels the oil storage chamber pressure and pushes up, and pressure is let out earlier to first draining passageway, forms the buffering, also can stably close the door. The oil return needle is arranged in the valve needle assembly, the valve needle assembly further comprises a spring and a valve needle, and at least one section of thin part and the thick part at the lower end of the whole thin part of the oil return needle penetrate out of the valve needle. The height position of the oil return needle in the mandrel is set by screwing in or screwing out the adjusting screw in the main body screw. When taking place the violence and closing the door, the piston moves up, and oil storage chamber space is compressed, and the oil pressure increase, needle experience oil storage chamber pressure upwards backs down the spring, and the spring is flexible according to the size of oil storage intracavity oil pressure, and the volume of contracting in the needle changes along with oil storage chamber pressure change, then the size of control hydraulic pressure oil flow, forms the buffering. Therefore, the fact that the pressure of the oil storage cavity is too high means that the pressure of the oil storage cavity exceeds the preset pressure of the spring, and when the pressure of the oil storage cavity exceeds the preset pressure of the spring, the valve needle retracts inwards to open the first oil drainage channel. When the spring structure of the valve needle assembly meets violent force to open and close the door, even if the force is applied to the valve needle assembly to a great extent, the conditions of damage of parts and damage of a door body can not be generated, and the service life of the hydraulic hinge is prolonged. When the piston moves upwards, a gap is formed between the thin part and the speed regulating valve hole of the piston, and when the piston moves downwards, the thick part limits the flow of the speed regulating valve hole. The C-shaped clamp spring is arranged for the following performance of the valve needle, and if the C-shaped clamp spring is not arranged, the main body screw is upwards adjusted, and the valve needle cannot leave the oil hole. With the upward fine adjustment of the C-shaped clamp spring, the valve needle can separate the oil hole upwards along with the main body screw.

Furthermore, a wave-shaped track is formed between the cylinder body fixedly arranged in the main body pipe and the lower cam ring, the side wall of the piston is provided with a sliding sleeve which is guided to slide in the wave-shaped track, the connecting main shaft is connected with the piston, the connecting main shaft rotates to drive the piston to rotate in any direction from left to right, and the piston axially moves under the guide of the sliding sleeve. Can be in order to realize the piston axial displacement under the effect of the pressure differential of oil storage chamber and hydraulic pressure oil storage bin, the utility model provides a lower cam ring, the cylinder body is with lower cam ring's theory of operation, when the door is closed, the dabber is in when initial condition, the sliding sleeve stops on the orbital crest top dead center of wave form, the in-process of opening the door, it is manual with the door open, connect the main shaft and rotate, it drives the piston rotation to connect the main shaft, the piston with connect the main shaft syntropy rotatory, the sliding sleeve prolongs the orbital motion that forms between cylinder body and the lower cam ring this moment, also follow crest top dead center and get off, the sliding sleeve moves down and the piston is the downstream also, the one end that shows for aforementioned piston rotates one side and is close to the main spring under the drive of connecting the main shaft promptly. When the door is opened to 90 degrees, the sliding sleeve moves to the lower dead point at the wave trough, the main spring is gradually reset in the door closing process, the sliding sleeve moves to the upper dead point at the wave crest again, and the piston moves to one end close to the oil return needle while rotating under the driving of the connecting main shaft. The butt joint structure of the horizontal plane at the bottom of the cylinder body and the horizontal plane at the top of the lower cam ring ensures that the door body stably stays at 90 degrees when the door is opened.

Furthermore, the sliding sleeve is a cam sliding sleeve, the side wall of the piston is provided with a track sliding needle hole, and a track sliding needle is arranged in the track sliding needle hole and is sleeved with the cam sliding sleeve. The piston is fixedly provided with a sliding sleeve through a track sliding needle, the sliding sleeve of the second embodiment is a cam sliding sleeve, the track sliding needle is designed into a shape corresponding to the cam sliding sleeve, and the sliding sleeve can run more smoothly due to the matching of the track sliding needle and the sliding sleeve.

Further, the main shaft is connected with the piston in a spline mode. The connecting main shaft and the piston are arranged in a tooth-to-tooth meshing manner, and the spline position structure is the tooth-to-tooth meshing structure. The bottom of the piston is provided with a spline slot, a main shaft spline connecting position is arranged on the connecting main shaft, the main shaft spline connecting position and the spline slot are installed in a tooth-to-tooth meshing mode, the connecting main shaft rotates to drive the piston to transmit, and the connecting main shaft is connected with the piston in a driving mode.

And further, an outer oil groove of the piston communicated with the main oil way is formed in the outer wall of the piston, and the outer oil groove of the piston is communicated with the hydraulic oil bin and the one-way valve. When pressure difference is generated, oil flows through the main oil way, and simultaneously, the oil can also flow into the piston through the oil groove outside the piston and flows into the oil storage bin through the one-way valve.

Furthermore, one end of the connecting main shaft, which is far away from the piston, is provided with a screw hole, an adjusting groove penetrating through the screw hole is formed in the rod wall of the end of the connecting main shaft, the adjusting groove extends along the axial direction of the connecting main shaft, a spring ejector pin capable of sliding along the adjusting groove is inserted into the adjusting groove, the main spring is abutted between the bottom of the piston and the spring ejector pin, a spring adjusting screw is connected with the screw hole in a screwed mode, and the end portion of the spring adjusting screw is abutted to the spring ejector pin. The depth of the spring adjusting screw in the screw hole is changed by twisting the spring adjusting screw, so that the position of the spring adjusting screw can be adjusted, the tightness of the main spring is adjusted, and the door closing force is changed.

Furthermore, the pressure positioning sleeve comprises a pressure positioning sleeve and a plurality of steel balls, the pressure positioning sleeve is sleeved on the lower portion of the connecting main shaft, protruding edges extend out of the periphery of the connecting main shaft, annular pit grooves are formed in opposite surfaces of the pressure positioning sleeve and the protruding edges respectively, the steel balls are placed in the annular pit grooves, the inner wall of the main pipe is sunken to form positioning grooves, and the pressure positioning sleeve abuts against the positioning grooves. The pressure location sleeve functions to locate to determine the stability of the internal structure.

Further, the wave-shaped track is formed by a wave crest and a wave trough within the 180-degree circumferential range, and a sliding sleeve is installed on the piston. The hydraulic hinge can be used for a 180-degree door, and two sides of the door are opened.

Further, the wave-shaped track is formed by two pairs of wave crests and wave troughs in a 360-degree circumferential range, and two sliding sleeves are oppositely arranged on the piston for 180 degrees. The rotating range of the hinge is increased, and the hydraulic hinge can be used for a 360-degree door.

Compared with the prior art, the beneficial effects of the utility model reside in that, the door is slowly closed, reaches the cushioning effect. When in use, the door closing speed is stable. Especially meet the condition that the door was closed to the violence, the atress is great when beginning promptly, leads to the oil pressure too big, and the needle can feel the oil storage chamber pressure and push up, and pressure is let off earlier to first draining passageway, forms the buffering, stably closes the door. By adjusting the height position of the oil return needle in the mandrel, the closing angle of the mandrel at the inertia force stage during closing can be adjusted, and the adjustment of the door closing speed is realized. The size of the oil passing amount of the speed regulating valve hole is adjusted, and the buffering is provided when the door is opened and closed. The utility model discloses speed governing off-load oil return needle subassembly is closing the door and reaching quick pressure release at the correspondence violence, makes hydraulic structure more stable, avoids hydraulic cylinder pressure too big to cause the structure damage, avoids single passageway to use the loss to equipment, reduces the maintenance rate, increase of service life.

Drawings

Fig. 1 is an exploded view of the mandrel structure of the present invention.

Fig. 2 is an exploded view of the valve needle assembly structure of the present invention.

Fig. 3 is a schematic view of the hydraulic oil passage inside the piston.

Figure 4 is a side view of the spindle with the door 90 open.

Fig. 5 is a front view of the spindle with the door 90 ° open.

Fig. 6 is a side view of the spindle with the door closed.

Fig. 7 is a schematic view of hinge positioning and door stopper function angle intervals.

FIG. 8 is a side view of the hydraulic hinge with the door closed.

Fig. 9 is a side view of the hydraulic hinge with the door 90 open.

Fig. 10 is a front view of the hydraulic hinge with the door 90 open.

The drawing comprises a main pipe 1, an upper cam positioning groove 11, a lower cam positioning groove 12, a cam group depth positioning groove 13 and a pressure positioning sleeve depth positioning groove 14; the oil seal structure comprises a valve needle assembly 2, a main body screw 21, a spring 22, a valve needle 23, a C-shaped clamp spring 24, an adjusting screw 25, an oil return needle 26 and a first oil seal pit 27; the device comprises a cylinder body 3, an adjusting screw position 31, a main pipe sealing pit 32, a first main pipe oil sealing pit 33, a pressure cylinder 34, an upper cam positioning pit 35, an upper cam rim 36, a pressure relief hole 37, a cone valve hole 38 and strong magnetic particles 39; the device comprises a piston 4, a speed regulation valve hole 41, a track sliding needle hole 42, a track sliding needle 43, a sliding sleeve 44, a one-way valve 46, an oil through hole 47, a second oil seal pit 48 and a piston outer oil groove 49; lower cam ring 5, lower cam positioning pit 51, lower cam rim 52; the connecting main shaft 6, a main shaft spline connecting position 61, a main oil way 62, a third oil seal pit 63, a convex edge 64, an upper pressure ball pit groove 65 and a connecting spline 66; a main spring 7; a main spring adjusting mechanism 8, a spring adjusting screw 81, a spring thimble 82 and a fourth oil seal pit 83; the pressure positioning sleeve 9, the bearing positioning sleeve 91, a lower pressure ball pit groove 92, a second main pipe oil seal pit 93 and a positioning pit 94; a hydraulic oil sump 10.

Detailed Description

The present invention will be further described with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

As shown in fig. 1, a mandrel comprises a main tube 1, a valve needle assembly 2, a cylinder 3, a piston 4, a lower cam ring 5, a connecting main shaft 6, a main spring 7, a main spring adjusting mechanism 8 and a pressure positioning sleeve 9.

The diameters of the outer walls of all the parts of the main pipe 1 are kept consistent, and the inner wall is provided with grooves for positioning, wherein the grooves comprise an upper cam positioning groove 11, a lower cam positioning groove 12, a cam group depth positioning groove 13 and a pressure positioning sleeve depth positioning groove 14. The cam groove 11 corresponds to the upper cam groove 35 in the cylinder 3 and the lower cam groove 12 and cam set depth groove 13 correspond to the lower cam groove 51 of the lower cam ring 5. The pressure positioning sleeve depth positioning groove 14 corresponds to the pressure positioning sleeve 9.

The valve needle assembly 2 shown in fig. 1 and 2 comprises a main body screw 21, a spring 22, a valve needle 23, a C-shaped clamp spring 24, an adjusting screw 25 and an oil return needle 26. The center of the main body screw 21 is provided with a speed regulating valve hole, an adjusting screw 25 is arranged in the speed regulating valve hole, the lower part of the adjusting screw 25 is connected with one end of the oil return needle 26, and the outer wall of the speed regulating valve hole is sleeved with a spring 22. The inside of the main body screw 21 is also provided with a C-shaped snap spring 24, and the valve needle 23 is arranged below the spring 22 through clamping connection with the C-shaped snap spring 24. The other end of the oil return needle 26 passes through the valve needle 23, and at least a section of the thin part is exposed outside the valve needle 23. The valve needle assembly 2 is further provided with a first oil seal pit 27 on the main body screw 21 and the adjusting screw 25 respectively. The oil return needle 26 comprises a thin part at the middle and thick parts at two ends, wherein the thick part below the thin part is variable in diameter.

An adjusting screw position 31 is arranged at one end of the cylinder body 3, and the outer wall of the main body screw 21 is matched with the inner wall of the adjusting screw position 31. The valve needle assembly 2 is mounted on the upper end of the cylinder 3 through the main body screw 21 and the adjusting screw position 31. A main pipe sealing pit 32 and a first main pipe oil sealing pit 33 are respectively arranged on two sides of the adjusting screw position 31, a pressure cylinder 34 is arranged at the other end of the cylinder body 3, upper cam positioning pits 35 are arranged on two sides of the pressure cylinder 34, and an upper cam edge 36 is arranged at the bottom of the pressure cylinder. The adjusting screw position 31 is communicated with the pressure cylinder 34 through a cone valve hole 38, and a pressure relief hole 37 is formed in the side wall of the cone valve hole 38. The inner cavity of the cylinder body 3 is provided with a magnetic particle bin, and the inner device of the cylinder body is provided with strong magnetic particles 39 which are used for filtering and adsorbing impurities in oil, so that the smoothness of an oil path is ensured, the service life is prolonged, and the maintenance rate is reduced.

The bottom of the cylinder body 3 is provided with an upper cam edge 36, the upper cam edge 36 comprises a wave crest and a wave trough in a 180-degree circumference, and in order to increase the rotation range of the hydraulic hinge, the bottom of the cylinder body can also comprise two pairs of wave crests and wave troughs in a 360-degree circumference. Lower cam ring 5 both sides are lower cam locating hole 51, the lower cam of top shape is along 52 the same with upper cam along 36, cylinder body 3 and lower cam ring 5 respectively fixed mounting inside casing 10, form the wave form track between cylinder body 3 and the lower cam ring 5, two kinds of cylinder body bottom shapes form single wave peak track and two wave peak tracks respectively, single wave peak track has a crest and trough at 180 semicircle within range, two wave peak tracks have two crests and troughs at 360 circumferences, wherein the crest is top dead center, the trough is bottom dead center. The upper stop position is provided with a circular arc structure.

The cylinder 3 comprises a pressure cylinder 34, the piston 4 penetrates upwards from the bottom of the cylinder 3, and the closed cavity between the piston 4 and the cylinder 3 forms an oil storage cavity, namely the cavity separated from the top end of the piston 4 in the pressure cylinder 34 is the oil storage cavity. The side wall of the piston 4 is provided with a track sliding needle hole 42, and a track sliding needle 43 is arranged in the track sliding needle hole 42. The piston 4 is fixedly provided with a sliding sleeve 44 through a track sliding needle 43, and the sliding sleeve 44 is arranged between the cylinder 3 and the lower cam ring 5 to form a wave track. The sliding sleeves 44 are guided to slide in the wave-shaped track, one sliding sleeve 44 is arranged in the single wave track, and two sliding sleeves 44 are arranged in the double wave track. The arc structure arranged at the top dead center position is used for stopping when the sliding sleeve 44 moves to the top dead center. The piston 4 is fixedly provided with a sliding sleeve 44 through an orbital sliding needle 43. The sliding sleeve 44 shown in fig. 1 is a cam sliding sleeve 44, and the rail sliding needle 43 is designed to have a shape corresponding to the cam sliding sleeve 44, and the engagement of the rail sliding needle 43 with the sliding sleeve 44 makes the sliding sleeve 44 operate more smoothly.

Fig. 3 is a schematic diagram of a hydraulic oil passage inside the piston 4, a main oil passage 62 is formed in the piston 4, a speed regulation valve hole 41 communicated with the main oil passage 62 is formed in the top of the piston, a check valve 46 communicated with the main oil passage 62 is installed, and an oil inlet passage is formed by the check valve 46. The piston 4 is provided with an oil through hole 47 and an outer piston oil groove 49, and the outer piston oil groove 48 is communicated with the hydraulic oil bin 10 and the one-way valve 46. The flow direction of the hydraulic oil is shown by an arrow, the middle of the upper part of the piston 4 is provided with a speed regulating valve hole 41 communicated with the connecting main shaft 6 and is also a part of the main oil path 62, and the hydraulic oil flows into the one-way valve 46 from the main oil path 62 and then flows into the oil storage cavity. The hydraulic oil can also flow from the hydraulic oil sump 10 into the oil through hole 47 through the oil groove 49 outside the piston, then into the check valve 46, and then into the oil storage chamber. The middle of the upper part of the piston 4 is a speed regulation valve hole 41, and a second oil drainage channel is formed by a gap between the detail part of the oil return needle 26 and the speed regulation valve hole 41.

The piston 4 is in driving connection with the connecting main shaft 6, so that the connecting main shaft 6 rotates to drive the piston 4 to rotate in either left or right direction, and the piston 4 can move axially under the guidance of the sliding sleeve 44. Specifically, the connecting main shaft 6 and the piston 4 are installed in a tooth-to-tooth meshing manner, and the spline structure is the tooth-to-tooth meshing structure. The bottom of the piston 4 is provided with a spline slot, the connecting main shaft 6 is provided with a main shaft spline connecting position 61, the main shaft spline connecting position 61 and the spline slot are installed in a tooth-to-tooth meshing manner, the connecting main shaft 6 rotates to drive the piston 4 to transmit, and the connecting main shaft 6 is in driving connection with the piston 4.

The adjustable spring type spring loading mechanism comprises a main spring adjusting mechanism 8 shown in fig. 1, wherein the main spring adjusting mechanism 8 comprises a spring adjusting screw 81 and a spring ejector pin 82, one end of a connecting main shaft 6 far away from a piston 4 is provided with a screw hole, an adjusting groove penetrating through the screw hole is formed in the rod wall of the end, the adjusting groove extends along the axial direction of the connecting main shaft 6, the adjusting groove is internally inserted with the spring ejector pin 82 capable of sliding along the adjusting groove, a main spring 7 is abutted between the bottom of the piston 4 and the spring ejector pin 82, the screw joint of the screw hole is provided with the spring adjusting screw 81, and the end part of the spring adjusting screw 81 is abutted to the spring ejector pin 82. The spring adjusting screw 81 is provided with a left fourth oil seal pit 83 and a right fourth oil seal pit 83.

The end of the connecting main shaft 6 is sleeved with a connecting spline 66, and the connecting spline 66 is used as a connecting piece between the hinge and the connecting main shaft 6. The spring adjusting screw 81 screwed in the screw hole is sleeved in the connecting main shaft 6. The upper part of the connecting position of the connecting main shaft 6 on the connecting spline 66 is provided with a third oil seal pit 63 at the lower part of the convex edge 64.

The pressure positioning sleeve 9 is characterized by further comprising a pressure positioning sleeve 9, the pressure positioning sleeve 9 comprises a pressure positioning sleeve 9 and a plurality of steel balls, the center of the pressure positioning sleeve 9 is a bearing positioning sleeve 91, the lower portion of the main shaft 6 is connected in a sleeved mode through the bearing positioning sleeve 91, the periphery of the main shaft 6 is connected with a protruding edge 64 in an extending mode, the opposite surfaces of the pressure positioning sleeve 9 and the protruding edge 64 form annular pit grooves respectively, the pit groove on the protruding edge 64 is an upper pressure ball pit groove 65, the annular pit groove on the pressure positioning sleeve 9 is a lower pressure ball pit groove 92, the steel balls are placed in the upper pressure ball pit groove 65 and the lower pressure ball pit groove 92, the inner wall of the main pipe 1 is sunken to form a positioning groove, namely the pressure positioning sleeve depth positioning groove 14, and the pressure positioning sleeve 9 abuts against the pressure positioning sleeve depth positioning groove 14. The side wall of the pressure positioning sleeve 9 is also provided with a plurality of second main pipe oil seal pits 93 and positioning pits 94.

The utility model discloses an operating principle does, and when the door was closed, the dabber when being in initial condition, sliding sleeve 44 stopped on the stop at orbital crest place of wave form. During the door opening process, the door is manually opened, the connecting main shaft 6 rotates, at the moment, the sliding sleeve 44 moves along a wave-shaped track formed between the cylinder body 3 and the lower cam ring 5, namely, the sliding sleeve 44 moves down from the top dead center of the wave crest, and the piston 4 also moves downwards due to the guiding effect of the sliding sleeve 44. In short, the piston 4 is moved to the end close to the main spring 7 while being rotated by the connecting main shaft 6. The oil return needle 26 is fixed, when the piston 4 moves, the thick portion limits the flow of the speed regulating valve hole 41 of the piston 4, the second oil drainage channel is limited, meanwhile, the main spring 7 is compressed due to the movement of the piston 4, the oil storage cavity space expands, the oil pressure is reduced, the hydraulic oil of the hydraulic oil bin 10 enters from the oil inlet hole connected with the main shaft 6, the oil inlet hole is not shown in the figure, as shown in fig. 4, the hydraulic oil flows into the oil storage cavity from the check valve 46 of the piston 4 through the main oil channel 62 to the piston 4, and the other hydraulic oil flows into the check valve 46 through the oil through hole 47 from the oil groove 49 outside the piston and then flows into the oil storage cavity. Fig. 4 and 5 show a side view and a front view, respectively, of the spindle with the door open at 90 deg.. As can be seen from fig. 4 and 5, when the sliding sleeve 44 has moved to the bottom dead center where the wave trough is located, the oil storage cavity is filled with hydraulic oil, the thick portion of the oil return needle 26 is located in the speed regulation valve hole of the piston 4, and the door stably stays at 90 °.

In the process of violently closing the door, the main spring 7 compresses and applies an upward force to the piston 4, the sliding sleeve 44 moves to the top dead center at the wave crest again, the piston 4 rotates under the drive of the connecting main shaft 6 and moves towards one end close to the oil return needle 26 at the same time, pressure is applied to oil in the oil storage cavity, the oil pressure in the oil storage cavity is increased, when the pressure of the oil storage cavity generated by the violence exceeds the preset pressure of the spring 22, the valve needle 23 moves upwards to apply the upward pressure to the spring 22, the valve needle 23 jacks up, hydraulic oil flows back to the hydraulic oil bin 10 from the first oil drainage channel where the pressure relief hole 37 is located, as shown by an arrow on the right side of fig. 4, buffering is achieved, and the hydraulic effect is fast and slow. As the violence decays and the hydraulic oil flows out, the valve needle 23 descends to block the pressure relief hole 37, and the first oil release passage is closed. And the hydraulic oil in the rest oil storage cavity flows out through the second oil drainage channel. The piston 4 moves to enable the oil return needle 26 to be located in the speed regulation valve hole 41, hydraulic oil in the oil storage cavity is drained outwards through the second oil drainage channel, the thin part of the oil needle is a quick oil drainage level, and the thick part of the oil needle is a slow leakage position. The axial movement of the piston is slowed down, so that the door is slowly closed to achieve the buffering effect. As shown in fig. 6, which is a side view of the mandrel in the closed state of the door, it can be seen from fig. 6 that the sliding sleeve 44 stays at the peak top dead center of the wave orbit and the oil reservoir is almost completely compressed.

In the normal door closing process, the door self-closing under main spring 7's resilience force effect, main spring 7 resets gradually, sliding sleeve 44 removes to the top dead center that is in the crest again, piston 4 rotates on one side under the drive of connecting the main shaft and moves to the one end that is close to oil return needle 26 on one side, there is not the process that needle 23 was jacked, piston 4 removes and makes oil return needle 26's thin part be in speed governing valve hole 41, the hydraulic oil of oil storage chamber passes through speed governing valve hole 41 and outwards lets out oil, oil needle thin part is the quick oil level of discharging, thick portion reducing is the slow position of leaking outward. The door is slowly closed to achieve the buffer effect.

The utility model provides a dabber is under the normal state of closing the door, only through the 26 draining of oil return needle, when meetting the violence and closing the door, needle 23 is because of pressure by jack-up, from the 37 draining of pressure release hole, then from the 26 draining of oil return needle again. The door is slowly closed, and the buffer effect is achieved. Meet the condition that the violence was closed the door, the atress is great when beginning promptly, leads to the oil pressure too big, and needle 23 can experience the up-pushing of oil storage chamber pressure, and pressure is let off earlier to first draining passageway, forms the buffering, stably closes the door. The door closing speed can be adjusted by the return needle 26. The oil return needle 26 is fixed, but the height position of the oil return needle in the mandrel is adjusted by moving up and down through screwing in and out of the main body screw 21 and the adjusting screw 25, the thin part of the oil return needle 26 is the quick oil discharge level, the length of the quick oil discharge level is changed by adjusting the height position of the oil return needle 26 in the mandrel, the closing angle of the mandrel in the inertia force stage during closing is adjusted, and the door closing speed is adjusted. Since the thick portion of the oil return needle 26 shown in fig. 1 is variable-diameter, when the door is closed, the thinner portion of the thick portion is decompressed, and the thinner portion is completely decompressed.

As shown in fig. 7, the present invention provides a mandrel with two modes of locking and silencing. The thick part is a hydraulic buffer position, and the thin part is an instant discharge position. The detailed function is that quick oil discharge is equivalent to no hydraulic buffer. The rear section door closing angle is favorable for inertial locking, which is called a locking function. The lower end of the thin portion is actually completely discharged when passing through the position of the speed valve hole 41. The details are completely adjusted, and basically, the thick part is called a full-section closing hydraulic buffering mode. The silent mode is basically a full line bold. The oil return needle 26 is set at a certain height position in the mandrel, and the effect is that when the door is closed, the door reaches the position of about 25-30 degrees from the door frame, and the thin part is positioned in the speed regulation valve hole to quickly discharge oil to form inertia force locking. The range of 25 ° to 30 ° is a value that can be configured to a desired inertial door closing angle, for example, 10 or 15 °, if the setting is full-buffer, i.e., the silent mode described above. As shown in fig. 6, the inertia force locking mode or the silent door closing mode can be adjusted within 0 ° to 15 °.

The valve needle 23 and the oil return needle 26 are installed on the valve needle assembly 2, the valve needle assembly 2 further comprises a spring 22 and the valve needle 23, at least one section of thin part and a thick part at the lower end of the complete thin part of the oil return needle 26 penetrate through the valve needle 23, the oil return needle 26 is fixed, and the valve needle 23 can move axially. When the door is opened and closed violently, even if the force is applied greatly, the conditions of damage of parts and damage of the door body cannot be generated, and the service life of the hydraulic hinge is prolonged.

The C-shaped clamp spring 24 is arranged for the following performance of the valve needle 23, and if the C-shaped clamp spring 24 is not arranged, the valve needle 23 cannot leave the oil hole when the main body screw 21 is upwards adjusted. With the upward fine adjustment of the C-shaped clamp spring 24, the valve needle 23 will follow the main body screw 21 to separate the oil hole upward.

The utility model discloses a connect 6 drive pistons 4 of main shaft and rotate, connect main shaft 6 and drive sliding sleeve 44 simultaneously and press orbital motion, sliding sleeve 44 provides the ascending direction of axial for piston 4. The track is of a wave structure, the piston 4 can move in any direction according to the rotation direction of the connecting main shaft 6, and the hydraulic hinge can work in all directions in mounting and use. Preferably, the wave-shaped orbit is formed by a wave crest and a wave trough within a circumference of 180 °, and a sliding sleeve 44 is installed on the piston 4. The hydraulic hinge can be used for a 180-degree door, and two sides of the door are opened. The wave-shaped track is formed by two pairs of wave crests and wave troughs within the circumferential range of 360 degrees, and two sliding sleeves 44 are oppositely arranged on the piston 4 at 180 degrees. The rotating range of the hydraulic hinge is increased, and the hydraulic hinge can be used for a 360-degree door. The butt joint structure of the upper cam edge 36 at the bottom of the cylinder body and the lower cam edge 52 at the top of the lower cam ring 5 enables the door body to stably stay at 90 degrees when the door is opened.

And a positioning piece and an oil seal position are arranged in the mandrel from top to bottom, so that the stability of internal parts is ensured, and the problem of oil leakage existing in the hydraulic hinge is solved. The positioning piece comprises a positioning component connected with the lower part of the main shaft 6 and a groove used for positioning in the main pipe 1. The oil seal locations shown in fig. 1 include the first oil seal pit 27 of the valve needle assembly 2, the second oil seal pit 48 of the piston 4, the third oil seal pit 63 connecting the main shaft 6, the first main pipe oil seal pit 33 and the main pipe oil seal pit 32 on the cylinder block, and the second main pipe oil seal pit 93 on the pressure locating sleeve 9.

A main spring adjusting mechanism 8 is arranged, and the tightness of the main spring 7 is adjusted through the arrangement of a spring adjusting screw 81. During the use, change its degree of depth in the screw through wrench movement spring adjusting screw 81, can adjust spring adjusting screw 81's position to adjust main spring 7's elasticity, with the change dynamics of closing the door.

The utility model discloses still provide the hydraulic pressure hinge that uses this dabber, the schematic structure is as shown in figure 8, figure 9 and figure 10, establish including dabber and cover the epaxial last hinge of hydraulic pressure hinge spindle and lower hinge. Fig. 8 is a side view of a hydraulic hinge in a door closed state, in which an upper hinge and a lower hinge are on the same plane, and fig. 9 and 10 are a side view and a front view, respectively, of a door opened by 90 °, in which the planes of the upper and lower hinges are 90 °. The hydraulic hinge is sleeved with an upper hinge sheet and a lower hinge sheet on the outer side of the mandrel, the upper hinge sheet is positioned and pressed in with a connecting spline 66 arranged at the top of the mandrel, the lower hinge sheet is pressed in with the connecting spline 66 arranged at the bottom of the mandrel and then is penetrated, and a non-standard pressure bearing is arranged in the middle for bearing. When the device is installed, the piston 4 is downward, namely the mandrel is reversely installed. Lower hinge is connected with connection main shaft drive 6, and the door is opening or the in-process of closing, and on the connection main shaft of lower hinge action transmission to dabber, the buffering effect of dabber also reacted to lower hinge, goes up hinge and main part pipe 1 fixed connection.

Finally, it should be noted that the above embodiments are merely representative examples of the present invention. Obviously, the present invention is not limited to the above-described embodiments, and many modifications are possible. Any simple modification, equivalent change and modification made to the above embodiments according to the technical spirit of the present invention should be considered as belonging to the protection scope of the present invention.

Claims (9)

1. The utility model provides an adjustable oil return speed's hydraulic pressure hinge dabber, includes main part pipe (1), cylinder body (3), piston (4), lower cam ring (5), main spring (7), connects main shaft (6) and pressure position sleeve (9), cylinder body (3), piston (4), lower cam ring (5), main spring (7), connection main shaft (6) and pressure position sleeve (9) top-down install in proper order in main part pipe (1), and piston (4) top is the oil storage chamber, and the below is hydraulic pressure oil bin (10), its characterized in that: a main oil way (62) is formed in the piston (4), a speed regulating valve hole (41) communicated with the main oil way (62) is formed in the top of the piston, a one-way valve (46) communicated with the main oil way (62) is installed, and an oil inlet channel is formed by the one-way valve (46); an adjusting screw position (31) is formed in the top of the cylinder body (3), the adjusting screw position (31) is communicated with the oil storage cavity through a cone valve hole (38), and a pressure relief hole (37) is formed in the side wall of the cone valve hole (38); the hydraulic hinge mandrel further comprises a valve needle component (2), the valve needle component (2) comprises a main screw (21), a spring (22), a valve needle (23), a C-shaped clamp spring (24), an adjusting screw (25) and an oil return needle (26), the main screw (21) is installed in an adjusting screw position (31), the center of the valve needle component is an accommodating hole, the adjusting screw (25) is installed in the accommodating hole, the oil return needle (26) is connected to the lower portion of the adjusting screw (25), the spring (22) is sleeved on the outer wall of the accommodating hole, the valve needle (23) is installed below the spring (22) through being clamped with the C-shaped clamp spring (24), the valve needle (23) is used for blocking a pressure relief hole (37), when the pressure in an oil storage cavity is too large, the valve needle (23) moves upwards, and the pressure relief hole (37) forms a first oil relief channel; the oil return needle (26) comprises a thin part in the middle and thick parts at two ends, the thick parts are variable in diameter, and a second oil drainage channel is formed in a gap between the oil return needle (26) and the speed regulation valve hole (41).

2. The hydraulic hinge mandrel as claimed in claim 1, wherein a wave-shaped track is formed between the cylinder body (3) and the lower cam ring (5) which are fixedly installed in the main body pipe (1), a sliding sleeve (44) is installed on the side wall of the piston (4) and slides in the wave-shaped track in a guiding manner, the connecting main shaft (6) is connected with the piston (4), the connecting main shaft (6) rotates to drive the piston (4) to rotate in any direction from left to right, and the piston (4) axially moves under the guiding of the sliding sleeve (44).

3. The hydraulic hinge mandrel as claimed in claim 2, wherein the sliding sleeve (44) is a cam sliding sleeve (44), and the side wall of the piston (4) is provided with a track sliding needle hole (42) in which a track sliding needle (43) is installed and is sleeved with the cam sliding sleeve (44).

4. Hydraulic hinge mandrel according to claim 1, characterised in that the main shaft (6) is splined to the piston (4).

5. The hydraulic hinge mandrel as claimed in claim 1, wherein an outer piston oil groove (49) communicated with the main oil passage (62) is formed in the outer wall of the piston (4), and the outer piston oil groove (49) is communicated with the hydraulic oil bin (10) and the check valve (46).

6. The hydraulic hinge mandrel as claimed in claim 1, wherein a screw hole is formed in one end of the connecting main shaft (6) far away from the piston (4), an adjusting groove penetrating through the screw hole is formed in the rod wall of the end, the adjusting groove extends in the axial direction of the piston rod, a spring ejector pin (82) capable of sliding along the adjusting groove is inserted in the adjusting groove, the main spring (7) abuts between the bottom of the piston (4) and the spring ejector pin (82), a spring adjusting screw (81) is screwed in the screw hole, and the end of the spring adjusting screw (81) abuts against the spring ejector pin (82).

7. The hydraulic hinge mandrel as claimed in claim 1, wherein the pressure positioning sleeve comprises a pressure positioning sleeve (9) and a plurality of steel balls, the pressure positioning sleeve (9) is sleeved on the lower portion of the connecting main shaft (6), a convex edge (64) extends from the periphery of the connecting main shaft (6), annular pit grooves are formed in opposite surfaces of the pressure positioning sleeve (9) and the convex edge (64) respectively, the steel balls are placed in the annular pit grooves, a positioning groove is formed in a concave portion of the inner wall of the main body pipe (1), and the pressure positioning sleeve (9) abuts against the positioning groove.

8. A hydraulic hinge mandrel as defined in claim 2 wherein said undulating path is defined by a peak and valley over a 180 ° circumference, and said piston is fitted with a sliding sleeve.

9. The hydraulic hinge mandrel as recited in claim 2, wherein the undulating path is defined by two pairs of peaks and valleys over a 360 ° circumference, and wherein two sliding sleeves are mounted 180 ° opposite each other on the piston.

Images