CN217389905U - A feeder hopper that is used for cherry to denucleate making beating device - Google Patents

Abstract

The utility model discloses a feeder hopper for cherry beating device that denucleates, including bar chamber and roller, the bar chamber is the contained angle along the box length direction that denucleates and with vertical direction and arranges and the inner and outer end is open structure, and bar chamber perpendicular to length direction staggered arrangement multirow rotatable roller, a bar chamber length direction bottom curb plate is provided with elastic telescopic baffle, and elastic telescopic baffle supports to lean on in feeding roller length direction. The utility model discloses a feeder hopper sets up crisscross multirow roller, and restriction cherry flow speed plays the effect that keeps cherry integrality, and the processing of denucleating of being convenient for sets up the flexible baffle of elasticity, prevents to fall the making beating mechanism for the cherry that denucleates from the gap between cylinder and the hopper.

Description

A feeder hopper that is used for cherry to denucleate making beating device

Technical Field

The utility model belongs to the technical field of the cherry making beating all-in-one that denucleates relates to a feeder hopper that is used for cherry making beating device that denucleates.

Background

The cherry is rich in nutrition, contains calcium, phosphorus, iron and various vitamins, and plays an important role in the fields of food and medical treatment. According to survey statistics, the agate red cherry is one of the fruits mainly produced in nine-hole days in Guizhou, and the cherry yield of every year is gradually increased when more than 2000 hectares are planted in the nine-hole-day cherry industry area. The cherry is difficult to store due to the short maturation period and the imperfect preservation technology. In order to realize the sustainable development of cherry industrialization, fruit growers process the cherry by using abundant local cherry resources, and research fruit wine, fruit juice and compound beverage to develop new cherry products.

The essential link in the process of developing the cherry fruit wine juice is to perform denucleation and pulping treatment on the cherry. At present, two links of denucleation and pulping in the market are separately carried out, generally, the denucleation is completed and then the paper pulp is transferred to a pulping device for pulping, and the transferring process consumes time and labor. The condition of mechanical assistance and manual work even replacing manual work appears in all trades nowadays, and in the field of cherry fruit wine and fruit juice, the requirement of the mechanical assistance and the manual work is very urgent, so that a device integrating cherry denucleation and pulping is needed to be researched.

The prior denucleation modes mainly comprise partial type, double-roller type, barrel rod type, beating type, scraper type, convex tooth roller separation concave plate type and the like, and the beating modes comprise vertical beating and horizontal beating. Horizontal spiral beating type of selecting mostly in the enterprise denucleates, this kind of mode easy operation that denucleates, and the making beating efficiency is fast, though this kind of mode collects denucleate and make beating as an organic whole, nevertheless can lead to the cherry stone broken, has reduced the quality of cherry fruit thick liquid, has lead to the taste of cherry fruit wine fruit juice to reduce. In order to improve the taste, a small number of enterprises can denucleate the cherry earlier before the making beating, transfer another device again after the completion of denucleating and make beating, but when denucleating, when the feeder hopper sent the cherry into the loading cylinder of mechanism of denucleating, can because the cherry fast butt joint that drops is in pay-off mouth department, can cause the extrusion because of the rotation of loading cylinder, can't keep complete form to be unfavorable for the processing of denucleating.

Disclosure of Invention

The to-be-solved technical problem of the utility model is: the utility model provides a feeder hopper that is used for cherry beating device that denucleates to solve the technical problem who exists among the prior art.

The utility model discloses the technical scheme who takes does: the utility model provides a feeder hopper for cherry beating device that denucleates, includes bar chamber and roller, the bar chamber along the box length direction that denucleates and be the contained angle with vertical direction and arrange and the inner and outer end is open structure, the rotatable roller of bar chamber perpendicular to length direction staggered arrangement multirow, bar chamber length direction bottom curb plate is provided with elastic telescopic baffle, elastic telescopic baffle supports to lean on loading drum length direction.

Preferably, above-mentioned loading drum both ends set up two ring guide rails, and the feeder hopper both ends inboard sets up two arc guide blocks, and the arc guide way internalization of two arc guide blocks has two ring guide rails and the outer cylinder of two ring guide rails and the medial surface of arc guide way that loading drum both ends set up to keep the clearance, and two arc guide blocks set up on the both ends lateral wall of feeder hopper.

Preferably, the elastic telescopic baffle is movably embedded into the strip-shaped blind hole in the side plate, the inner end of the elastic telescopic baffle is connected with a spring, and the inner end of the spring is connected to the bottom of the strip-shaped blind hole.

Preferably, the two side wall plates and the lower side wall plate of the feed hopper are of an integral wide groove structure, and the upper side wall plate covers the wide groove structure and is locked by screws.

The utility model has the advantages that: compared with the prior art, the utility model discloses an effect as follows:

(1) the utility model has the advantages that the feed hopper is provided with a plurality of staggered rows of rollers to limit the cherry flowing speed, play the role of keeping the integrity of the cherry, facilitate the denucleation treatment, and be provided with the elastic telescopic baffle plate to prevent the denucleated cherry from falling to the pulping mechanism from the gap between the roller and the hopper;

(2) the feeding roller both ends set up the ring guide rail, cooperate the arc guide block on the feeder hopper, cooperate two pairs of riding wheels, play directional rotatory effect on the one hand, on the other hand plays the effect of preventing the upset at the rotatory in-process of feeding roller.

Drawings

FIG. 1 is a schematic three-dimensional structure diagram of a cherry pit-removing and beating device;

FIG. 2 is a schematic view of another perspective structure of the cherry stone removing and beating device;

FIG. 3 is a schematic diagram of the right view structure of the cherry stone removing and beating device;

FIG. 4 is a schematic view of the cross-sectional structure A-A of FIG. 3;

FIG. 5 is a schematic view of the cross-sectional structure B-B in FIG. 4;

FIG. 6 is a perspective view of the lifting tool set;

FIG. 7 is a perspective view of the cutter;

FIG. 8 is a schematic view of a connection structure of the denucleation box body and the feed hopper;

FIG. 9 is a right side view schematic diagram of the denucleation box body and the feed hopper;

FIG. 10 is a schematic view of a rotated section A-A in FIG. 9;

FIG. 11 is a schematic view of the cross-sectional structure C-C of FIG. 10;

FIG. 12 is a schematic view of the cross-sectional view D-D of FIG. 10;

FIG. 13 is a schematic perspective view of a beating device;

FIG. 14 is a schematic sectional structure view of the beating device;

FIG. 15 is a perspective view of the batch mechanism;

FIG. 16 is a digital pyramid view;

FIG. 17 is a flow chart of the operation of the apparatus;

FIG. 18 is a plan view of the intermittent mechanism; in the figure, 1, a crank round pin; 2. a disc (a); 3. a disc (b); 4. a pin setting tooth; 5. the roller is connected with the disc; 6. a disc (c); 7. a roller round pin;

FIG. 19 is a schematic view of the motion of the crank pin and the pin tumbler teeth;

FIG. 20 is a force analysis diagram of the deadbolt tooth;

FIG. 21 is a circuit diagram of a motor of the control device;

FIG. 22 is a schematic view of the structure of the loading roller;

FIG. 23 is a schematic view of a screw press dry structure.

Detailed Description

The invention will be further described with reference to specific embodiments.

Example 1: as shown in fig. 1-21, a feeder hopper for cherry beating device that denucleates, this feeder hopper 2 includes bar chamber 201 and roller 202, bar chamber 201 along denucleate 1 length direction of box and with vertical direction be the contained angle arrange and the inside and outside end be open structure, bar chamber 201 perpendicular to length direction staggered arrangement multirow rotatable roller 202, bar chamber 201 length direction bottom curb plate is provided with elastic telescopic baffle 203, elastic telescopic baffle 203 supports and leans on in loading drum 302 length direction. In the flexible baffle 203 activity was embedded into the bar blind hole 205 on the curb plate, the inner was connected with spring 204, and spring 204 the inner is connected to bar blind hole bottom, and the lateral wall board thickness at bar chamber 201 both ends is big, is convenient for install the arc guide block, and the wide groove structure as an organic whole is managed with the lower side wall board to both sides, goes up the side wall board lid and closes structurally and adopt the screw locking at the wide groove, and this structure is convenient for install rotatory roller. The feeding hopper is a starting position for feeding fruit materials into the device, for the small-volume stone fruits such as cherries, when the processing quantity is large, in order to limit the quantity entering the stone removing mechanism, a round roller for limiting the cherry flow speed is added on the basis of a common feeding hopper, the roller installation principle is similar to the digital pyramid arrangement principle, as shown in fig. 16, the installed feeding hopper is shown in fig. 10 and fig. 12, in order to meet the feeding requirement at the lowest, the diameter of the roller is 10mm, and the distance between the cylinder and the cylinder is 30mm, so that the feeding hopper can enter medium cherries with the diameter within 20 mm; in order to prevent the cherry from falling to the pulping mechanism from the gap between the feeding roller and the feeding hopper for denucleating, an elastic telescopic baffle is additionally arranged on the lower side plate in the feeding hopper, and the whole length of the elastic telescopic baffle is slightly smaller than that of one side of the feeding roller and is arranged at the lowest side of the feeding hopper. When the feeding roller rotates, the baffle plate stretches along with the roller according to the change of the angle of one surface of the roller, and after the surface rotates, the baffle plate is quickly jointed with the next surface due to the action of the spring to quickly form a closed space, as shown in fig. 12.

Example 2: as shown in fig. 1-21, a making beating device for cherry denucleates, including the box 1 that denucleates, feeder hopper 2, mechanism 3 and the making beating device 4 denucleates, the box 1 that denucleates is installed at support 5 middle part, and feeder hopper 2 sets up the feed inlet in the top one side of the box 1 that denucleates, and mechanism 3 that denucleates installs on the box 1 that denucleates, and making beating device 4 is installed in support 5 bottom and is located the box 1 below that denucleates, and the discharge gate of the box 1 that denucleates is connected to the feed inlet of making beating device 4.

Preferably, above-mentioned mechanism 3 that denucleates is including going up and down to denucleate knife tackle 301, the loading cylinder 302 with go out nuclear hopper 303, be provided with the big step through-hole 304 that goes up to interior little from outer of depositing the cherry on the loading cylinder 302, install on two pairs of riding wheels 305 both ends bottom, one end is connected to actuating mechanism, the other end is the through-hole, the through-hole has inserted out nuclear hopper 303, it is provided with bar opening 306 to denucleate box 1 top, go up and down to denucleate knife tackle 301 and install in bar opening 306 top and go up and down the cutter of denucleate knife tackle 301 can just be to the step through-hole 304 of loading cylinder 302 top, go up and down to denucleate knife tackle 301 and also be connected to actuating mechanism, two pairs of riding wheels 305 fixed connection are in the box 1 that denucleates. The total pole number of the denucleation cutter bars of the lifting denucleation cutter group 301 is 5 multiplied by 32, and the denucleation efficiency is improved by 4 times compared with the single-row denucleation. When the stoning plate is operated, the stoning plate drives the stoning needle to move downwards to eject out the stone to complete the stoning operation. The power for realizing the up-and-down movement of the coring needle plate is provided by the rotation of the intermittent mechanism. As shown in fig. 15, a driving plate tooth is additionally arranged on the driven disc of the intermittent mechanism, and the driving plate tooth on the driven disc drives a round pin on the driving disc to drive the driving disc to rotate, so that the intermittent rotation and stop of the roller are realized; another round pin is connected with articulate one end, articulate other end and the needle leg joint that denucleates, the up-and-down motion of the needle that denucleates has been realized to the principle of adopting slider-crank motion, it includes the inclined groove to go out nuclear hopper 303, discharging pipe and V word strip mouth, V word strip mouth sets up at the inclined groove top, V word strip mouth width slightly is greater than the every planar width of octagonal roller, be convenient for collect the nucleolus of cherry, the discharging pipe sets up in inclined groove bottom, the inclined groove is through two spinal branch brace summer beams fixed connection on the crossbeam of support 5, the discharging pipe is through supporting on another crossbeam of mount fixed connection at the support.

Preferably, above-mentioned material loading cylinder 302 is octagonal cylinder, and cylinder circumference sets up to eight equallys divide the plane of denucleating promptly, and the plane of denucleating sets up step through-hole 304, and bar opening 306 is greater than the plane of denucleating, sets up circular cylinder into octagonal cylinder feed mechanism, and circular cylinder is equipped with the standing groove of stone fruit on the surface, and the pay-off that can only the single row denucleates, and the pay-off rate is lower. And the cylinder becomes octagon cylinder after the improvement, and each face of octagon cylinder has the cherry standing groove of multirow, has not only improved the pay-off rate, moreover the efficiency of denucleating also great improvement. As shown in fig. 12 and 22, the octagonal roller is mainly composed of an octagonal roller, a riding wheel, a gap driving mechanism, and the like. To reduce the gravitational force, the material of the rollers can be selected to be plastic rollers of sufficient strength.

Preferably, a cutter guide plate 307 is arranged at the strip-shaped opening 306, a guide through hole 308 is arranged on the cutter guide plate 307, and the guide through hole 308 can be opposite to the step through hole 304. Set up the cutter deflector, on the one hand take the cherry away from the cherry standing groove after accomplishing in order to prevent denucleating to the cherry, influence the efficiency of making beating, on the other hand, play guide bar's effect, it is crooked to avoid the guide bar to strike the too big emergence of nucleolus in-process atress, improve the cutter and denucleate impact stability, as shown in fig. 3.9, aperture on the cutter deflector is the concentric circle with the standing groove of cylinder, unanimous with the diameter of minimum hole diameter and coring needle second section, the whole length of this board is the same with the cylinder one side with the width, install it on the last box of cylinder.

Preferably, above-mentioned lift knife tackle 301 that denucleates includes many cutters 309, cutter mounting panel 310, suspension support 311 and guide bar 312, suspension support 311 both ends are passed through the vertical swing joint of guide bar 312 on support 5, cutter mounting panel 310 is connected at suspension support 311 lower extreme, many cutters 309 pass through screw fixed connection on cutter mounting panel 310 and just to step through-hole 304, suspension support 311 includes the crossbeam, crossbeam middle part below sets up the sand grip of rectangular shape, the sand grip both ends are connected to cutter mounting panel both ends through three integrative handstand V font trusses, still be provided with the binaural structure of articulated connecting rod on the crossbeam, efficiency is higher for making the kernel denucleate, can more rapidly scratch the peel in the process of denucleating, in time ejecting the kernel, consequently, improve the cutter of denucleating. Every cutter 309 includes the cutter arbor linkage segment 323 of the integrative structure that sets up from the top down, cutter arbor guide segment 324 and toper section 325 are provided with along its length direction and inlay groove 326, it imbeds and is fixed with cutting edge 327 and its cutting part protrusion toper section 325 to inlay groove 326 symmetry, cutting edge 327 both sides front end is the arc structure, middle part connection cutter arbor guide segment 324 and toper section 325 department thickness suit with inlay the groove width, adopt screw locking after the groove is inlayed, the cutter of denucleating divide into the three-section: the first section is larger in diameter (the cutter bar connecting section) so as to meet the maximum impact strength and prevent the cutter from being broken; the second section is a transition section (a cutter bar guide section) which is a part for connecting the cutting edge with the root of the cutter; the third segment is a blade portion (a tapered segment and a convex blade) which has an overall width slightly smaller than the diameter of the second segment, and the three segments constitute the coring tool, and the overall structure is shown in fig. 7.

Preferably, the driving mechanism comprises a driving motor 313, a transmission 314, a crank disk 315, a connecting rod 316, a tooth shifting disk 317 and a sheave plate 318, the driving motor 313 and the transmission 314 are both mounted on the support, the input end of the transmission 314 is connected to the motor shaft of the driving motor 313 through a belt mechanism, the crank disk 315 and the tooth shifting disk 317 are of an integral structure, the middle is connected through a cylindrical section, a limiting annular groove 318 is formed between the crank disk 315 and the tooth shifting disk, the crank disk 315 is connected to a suspension bracket 311 of the lifting coring cutter set 301 through the connecting rod 316 hinged to the crank disk, the tooth shifting disk 318 is provided with a shifting tooth 319, the middle of one end face of the sheave plate 318 is fixedly connected to a driving shaft 320 arranged in the middle of one end of the loading roller 302, and a plurality of shifting tooth rods 328 meshed with the shifting tooth 319 are uniformly arranged in the circumferential direction at intervals on the other end face of the sheave plate 318. In order to allow the coring mechanism sufficient time for coring, it is necessary to control the rotation and rest of the octagonal drum, and therefore, an intermittent mechanism consisting of the crank disk 315, the connecting rod 316, the tooth-dialing disk 317 and the sheave plate 318 is selected for implementation. The selected intermittent mechanism model is shown in fig. 4 and 15. The intermittent mechanism can meet the control requirement and is composed of three parts, wherein the first part is a part of intermittent drive plates connected with a motor, the second part is an intermittent disc, and the third part is a disc connected with a roller. The three parts form an intermittent mechanism and provide rotating power for the octagonal roller. The intermittent mechanism has the characteristics of simple structure, high mechanical efficiency and the like, can stably and intermittently rotate in the working process, and meets the requirements of not only rotating but also intermittently stopping the octagonal roller.

Preferably, two circular guide rails 321 are arranged at two ends of the feeding roller 302, two arc guide blocks 322 are arranged at inner sides of two ends of the feeding hopper 2, the two circular guide rails 321 are movably embedded into arc guide grooves of the two arc guide blocks 322, gaps are kept between outer cylindrical surfaces of the two circular guide rails 321 and inner side surfaces of the arc guide grooves, the two arc guide blocks 322 are arranged on side walls at two ends of the feeding hopper 2, each circular guide rail 321 is of a two-segment structure, namely a large segment 329 and a small embedding segment 330, two embedding strips 331 are arranged at two ends of the small embedding segment 330, two embedding grooves 332 are arranged at two ends of the large segment 329, the two embedding strips 331 are embedded into the two embedding grooves 332 and locked by screws, the structure is convenient for embedding the arc guide blocks for installation, as shown in fig. 22, two roller way 333 are further arranged on the feeding roller way near the inner sides of the two circular guide rails 321, the roller way is placed on the two pairs of supporting wheels, two pairs of riding wheels are arranged on the V-shaped side wall at the bottom of the denucleation box body, so that the feeding roller can rotate directionally.

Preferably, above-mentioned feeder hopper 2 includes strip chamber 201 and roller 202, and strip chamber 201 is the contained angle along 1 length direction of the box that denucleates and arranges and the inner and outer end is open structure with vertical direction, and the rotatable roller 202 of multirow is arranged in the crisscross of strip chamber 201 perpendicular to length direction, and a strip chamber 201 length direction bottom curb plate is provided with elastic telescopic baffle 203, and elastic telescopic baffle 203 supports and leans on material loading drum 302 length direction. The elastic telescopic baffle 203 is movably embedded into a strip-shaped blind hole 205 on the side plate, the inner end of the elastic telescopic baffle is connected with a spring 204, the inner end of the spring 204 is connected to the bottom of the strip-shaped blind hole, the side wall plates at two ends of the strip-shaped cavity 201 are large in thickness, an arc-shaped guide block is convenient to install, the two side wall plates and the lower side wall plate are of an integrated wide groove structure, the upper side wall plate covers the wide groove structure and are locked by screws, and the structure is convenient for installing a rotating roller. The feeding hopper is a starting position for feeding fruit materials into the device, for small-volume stone fruits such as cherries, in order to limit the number of the stone removing mechanisms entering the stone removing mechanism when the processing number is large, a circular roller for limiting the flow speed of the cherries is added on the basis of a common feeding hopper, the roller installation principle is similar to the digital pyramid arrangement principle, as shown in fig. 16, the installed feeding hopper is shown in fig. 10 and fig. 12, in order to meet the feeding requirement at the minimum, the diameter of the roller is 10mm, and the distance between the cylinder and the cylinder is 30mm, so that the feeding hopper can enter medium cherries with the diameter within 20 mm; in order to prevent the cherry from falling to the pulping mechanism from the gap between the feeding roller and the feeding hopper for denucleating, an elastic telescopic baffle is additionally arranged on the lower side plate in the feeding hopper, and the whole length of the elastic telescopic baffle is slightly smaller than that of one side of the feeding roller and is arranged at the lowest side of the feeding hopper. When the feeding roller rotates, the baffle plate stretches along with the roller according to the change of the angle of one surface of the roller, and after the surface rotates, the baffle plate is quickly jointed with the next surface due to the action of the spring to quickly form a closed space, as shown in fig. 12.

Preferably, above-mentioned making beating device 4 includes spiral juice extractor 401, feeder hopper 402 and collecting hopper 403, spiral juice extractor 401 fixed connection just is provided with the driving motor of driver action on support 5, feeder hopper 402 and collecting hopper 403 are installed respectively in the feed inlet at spiral juice extractor 401 top and the discharge gate department of bottom, feeder hopper 402 docks the discharge gate to denucleate box 1 bottom, one side behind the spiral extrusion of spiral juice extractor 401 is provided with waste residue discharge gate 404, spiral juice extractor is the machinery that can squeeze juice in succession. The spiral type juice extractor 401 comprises a squeezing spiral rod 405, a squeezing cavity 406, a cylindrical sieve 407, bearing seats 408 and a power device 409, wherein two ends of the squeezing spiral rod 405 are rotatably connected to the two bearing seats 408, one end of the squeezing spiral rod extends out and then is connected to the power device 409, spiral blade segments of the squeezing spiral rod 405 are positioned in the squeezing cavity 406, the upper end of the squeezing cavity 406 is communicated with a feed hopper 402, the lower end of the squeezing cavity 406 is communicated with a waste residue discharge port 404, the cylindrical sieve 407 is arranged at a waste residue outlet of the squeezing cavity 406 close to the squeezing spiral rod 405, the bearing seats 408, the squeezing cavity 406 and the power device are fixedly connected to a mounting plate 410, the mounting plate 410 is fixedly connected to a bracket 5, the power device comprises a beating driving motor and a transmission connected with the beating driving motor, and the feeding, pressing, pulp discharging and slag tapping are continuously performed in the working process of the beating device 4, the structure is simple, the shape is small, and the juice extracting efficiency is high, the operation is convenient. It mainly comprises a pressure device, a transmission device, a feeding device, a motor, a discharging device, a frame and the like, as shown in figures 13-14. In the working process of the device, feeding, pressing, discharging and discharging are continuously carried out. The juicing machine has the advantages of small appearance, simple mechanical structure, high juicing efficiency, high juice discharging speed and easy operation. The blade shape of the pressing screw of the screw juicer 401 is solid, annular, molded, or blade type. When dry granular and powdery materials are conveyed, solid blades are mostly selected; when blocky or viscous materials are conveyed, an annular blade is selected; when the material with higher toughness or compression is conveyed, the blade type or the forming type is selected, and the two blades are used for stirring, kneading and other technological operations on the material when the material is conveyed. The blades of the press screw are mostly made of steel plate or stainless steel, brass, aluminum, etc. When the material with larger corrosiveness is conveyed, the surface of the blade is covered with a layer of hard alloy such as tungsten, chromium, cobalt and the like or other similar anticorrosive materials, and the stainless steel is selected in the utility model. The cherries belong to granular materials, so a solid spiral is selected, and thick stainless steel is selected as the thickness of the blades. Considering that the cherry is pulped immediately after denucleation is finished without accumulation, according to the manufacturing characteristics of the screw rod, the manufactured screw rod needs to have a continuously increased inner diameter and a gradually reduced screw pitch, and the volume between adjacent blades is also gradually reduced. Because the screw pitch is small, the axial force applied to the material is increased, the radial force is reduced, and the squeezing and propelling of the fruit materials are promoted. The press screw is supported on the frame by a bearing block.

The spiral juicer mainly depends on a squeezing screw rod to do rotary motion in the cylindrical sieve, and the space between the cylindrical wall and the cylindrical sieve is reduced to squeeze materials, so that juice in the materials is squeezed out. The processing object of the patent is mainly agate red cherries, and the spiral rods with variable diameters and variable pitches are selected after comprehensive consideration. The spiral squeezing rod can be divided into five sections: the first section is a feeding part, the screw pitch of the first section is larger, and the first section is mainly used for smoothly feeding materials into the cylindrical screen; the second section is a prepressing part, the diameter of the second section is constant, but the screw pitch of the second section is gradually reduced, and the second section starts to carry out juicing operation on the materials; the third section and the fourth section are variable-diameter variable-pitch sections, and the sections are used for further squeezing the squeezed materials in the second section and forcibly squeezing the remaining juice; the fifth section is a slag discharging part, the section is not provided with a helical blade, and the section is in a round table shape in order to ensure that the slag discharging is smoother. The press screw pattern is shown in figure 23.

The cylindrical screen arranged at the bottom of the screw type juicer is generally made of a stainless steel plate which is rolled and then drilled. Considering the reasons of cleaning, disassembling and the like, the cylindrical screen is made into a semi-cylindrical screen, and the upper part and the lower part of the shell of the pulping mechanism are tightly pressed in the cylindrical wall. The pressure generated by the squeezing screw rod in the squeezing process can reach 1.2MPa, and the diameter of the sieve pores is generally set to be 0.3-0.8 mm in order to enable the cylindrical sieve to bear the pressure, and the diameter of the pores is selected to be 0.8mm in consideration of the strength of the cylindrical sieve. The cylindrical screen is shown in fig. 22. The part of the cylindrical sieve which is not perforated is the part of the cherry which falls to the beating mechanism after the kernel removal is finished, and the part is not beaten, so the perforation treatment is not carried out.

The utility model discloses a device can satisfy following process: the method mainly comprises the steps of feeding, positioning, feeding, removing cores, pulping and the like. In order to realize compact structure of the device, the two steps of cherry denucleating and beating are integrated, and a denucleating mechanism and a beating mechanism are integrated. The kernel removing mechanism of the device is arranged on the upper portion, the pulping mechanism is arranged on the lower portion, the whole structure is compact, the problem that time and labor are consumed when cherries are transferred is solved, and the situation that almonds are not smashed is guaranteed. The coring mechanism adopts a barrel rod type coring mode and is connected with the slider-crank to realize the up-and-down reciprocating motion of the coring mechanism. The making beating device adopts spiral juice extractor then, and spiral juice extractor can accomplish the back of denucleating at the stoner, can carry out rapid juice to the cherry, reaches the purpose of starching. The device is at the operation process at first that the octagon cylinder rotates the pay-off, and after reacing the assigned position, the mechanism of denucleating denucleates the cherry, and the mechanism of beating that drops after the cylinder is rotatory after the completion of denucleating beats the beating machine and carries out the making beating, and mutually noninterfere has realized the demand of denucleating and making beating integration in two mechanism working processes.

The device work flow is shown in figure 17 according to the design requirements.

Example 2: an operation method for a cherry stone removing and beating device comprises the following steps: the octagon cylinder rotates, sends into the vertical direction in top with the cherry in the feeder hopper, reachs the assigned position of the mechanism that denucleates after, the mechanism that denucleates the cherry, denucleates and accomplishes the back through the cylinder and fall the cherry flesh to the making beating mechanism and make the beating, and the cherry kernel is seen off.

The dynamics calculation of the cherry stone removing and beating device comprises the calculation of the stone removing efficiency of a stone removing machine and the calculation of the total power of a transmission system.

1. The denucleation efficiency of the denucleation machine takes agate red cherries as denucleation objects, the diameter range of the denucleation objects is 22-24 mm cherries, and cherry pits are flat ovate, 8-10 mm in length and 7-9 mm in diameter. According to the production flow, the requirement, the working principle and the like of the device, the denucleation efficiency mainly depends on the denucleation period T and the number T of the denucleation needles.

The theoretical denucleation efficiency is as follows:

in formula (1): m is the number of denucleated particles per hour;

t is the number of the denucleated needles;

t-pitting period.

The coring needle of the device is 5 multiplied by 32, namely 160 coring needles, and if the single coring period is 2s, the final result is that:

2. total power of transmission system

The power consumption of the device is mainly in three parts of kernel removal, feeding and beating. The power consumption of the three parts is different and is calculated below.

2.1 Power consumption of the corer System

The power of the system is transmitted by an intermittent mechanism, a round pin on a driven sheave of the intermittent mechanism is connected with the other end of a crank, the other end of the crank is connected with a kernel removing system, and the kernel removing mechanism is connected on a rack. When the driven grooved pulley rotates, the crank drives the coring mechanism to move up and down in a reciprocating manner. When the centers of the crank, the round pin and the driven grooved pulley are in a straight line to form the longest distance, the grooved pulley is stressed maximally at the moment, the length is about 360mm, the total weight of the whole coring mechanism during reciprocating motion is estimated to be 1000N, and the torque applied to the intermittent mechanism can be known by a torque formula:

T _from ＝F _{To get rid of} ·l＝1000×360×10 ^-3 ＝360N·m (3)

Therefore, the power consumed by the coring mechanism is:

in the formula (4), n _From -driven sheave rotational speed. Knowing n _From 30r/min, then:

therefore, the total power consumed by the system is:

in formula (5): eta ₁ -transmission efficiency of the cylindrical gear, taken as 0.98;

η ₂ the transmission efficiency of the speed reducer is 0.96;

η ₃ the transmission efficiency of the coupler is 0.98.

Substituting data into an equation (5) to obtain:

2.2 Power consumption of the feed System

The power of the feeding system is transmitted by the intermittent mechanism, and then the octagonal roller is driven to rotate. According to the volume and the material density of the octagonal roller, the total weight of the whole feeding system is estimated to be 1500N. The torque applied to the intermittent mechanism is known from the torque equation:

T _{master and slave} ＝F _Cartridge ·l (7)

In formula (7): l-the length of the intermittent mechanism to the center of mass of the drum.

Measurement l was 508mm, and data was substituted for formula (7):

T _main ＝F _Cartridge ·l＝1500×508×10 ^-3 ＝762N·m (8)

Therefore, the power consumed by the coring mechanism is:

in the formula (9), n _{Master and slave} -the rotational speed of the driving sheave in the intermittent mechanism. Knowing n _From 30r/min, i.e. n _{Master and slave} 30r/min, then:

therefore, the total power consumed by the system is:

in formula (11): eta ₁ -transmission efficiency of the cylindrical gear, taken as 0.98;

η ₂ the transmission efficiency of the speed reducer is 0.96;

η ₃ the coupling transmission efficiency is 0.98.

Substituting data into an equation (11) to obtain:

2.3 consumption of beating System

1. Selection of screw speed

According to the reference data, the rotating speed of the spiral juicer is low, and the rotating speed of the spiral rod is determined to be n which is 150r/min by referring to the rotating speeds of other juicers.

2. Determination of the pitch

The first section is a feeding screw, the initial pitch of the first section is determined to be l-40 mm according to the diameter of the cherry, and the pitches of other sections are decreased progressively.

Moving speed of the material:

juicing capacity of the screw juicer:

G＝3600δ ₀ v ₀ ρ ₁ φ (14)

in formula (14): g, productivity, namely taking G as 900kg/h according to the physical characteristics of the cherries;

δ ₀ -area of screw feed;

ρ ₁ bulk density of material, taking rho ₁ ＝400kg/m ³ ；

Phi, fill factor, is 0.3.

Substituting the parameters into the formula (14) to obtain:

according to an area formula of the feeding of the pressing screw rod:

in the formula (16), d ₂ -maximum diameter of the feed area of the press screw;

d ₁ -minimum diameter of the feed area of the press screw.

Estimate d ₁ Data were substituted for formula (4-16) at 60 mm:

3. power calculation

The power consumption of a screw juicer is mainly two parts: first, the power consumed to move the material; the second is the power consumed when pressing the material.

1) Power consumed while moving material:

in the formula (18), m represents the mass of the material;

t is the material moving time;

production capacity G.

Known as G900 kg/h, v ₀ The data are substituted into the formula (4-18) at 0.1 m/s:

2) power consumed when pressing material:

in the formula (20), Δ l represents the difference between the adjacent pitches;

z-number of pitches;

p _max the maximum pressure of the material is 1.2 MPa;

d ₂ -a helical outer diameter;

d ₁ -helical internal diameter.

Substituting the known data into an equation (20):

3) total power consumption:

in the formula (22), P ₃ -power consumed while moving material;

P ₄ -power consumed in pressing the material;

η ₁ -transmission efficiency of the cylindrical gear, taken as 0.98;

η ₂ the transmission efficiency of the speed reducer is 0.96;

η ₃ the coupling transmission efficiency is 0.98.

Substituting data into an equation (22) to obtain:

selection of motor and speed reducer

1. Motor selection

a. Power selection

From the foregoing, in order to provide sufficient torque, considering the losses of other energy of the motor during transmission, the machine design manual is consulted based on the calculated power values, and the rated power of the motor is selected to be 3 kW.

b. Rotational speed selection

The working rotating speed of the roller is 30r/min, the working rotating speed of the squeezing screw rod is 150r/min, and the machine design manual is consulted to know that the recommended transmission ratio range of the speed reducer is 8-30, so the available rotating speed range of the motor at the roller is 240-900 r/min, (8-30) x 30, the squeezing screw rod is 1200-4500 r/min, (750 r/min) the rotating speed of the motor at the roller is consistent with 1500r/min and 3000r/min, and the types of the motor corresponding to the squeezing screw rod are listed in the following table 1.

TABLE 1 technical parameters of the electric machine

Considering various factors comprehensively, the type of the motor at the selected roller is Y132M-8, the rated power of the selected motor is 3kW, and the full-load rotating speed is 710 r/min; the motor model at the position of the squeezing screw rod is Y100L2-4, the rated power of the selected motor is 3kW, and the full-load rotating speed is 1420 r/min.

2. Retarder selection

The total transmission ratio can be obtained by selecting the full-load rotating speed of the motor and the working rotating speed of each mechanism as follows:

when the two motors transmit power to the corresponding mechanisms, the power is transmitted after being decelerated by the speed reducer. After the total transmission ratio of each mechanism is calculated, the transmission ratio of each stage is reasonably distributed so as to reduce the load of transmission and improve the transmission precision. The gear transmission ratio of the upper part mechanism of the device is 1:2, so that the transmission ratio of the speed reducer is 11.8; and the gear transmission of the lower part mechanism is 1:1, so the transmission ratio of the speed reducer of the lower part is 9.47. According to the calculated transmission ratio, a mechanical design manual is consulted to know that the two-stage cylindrical gear speed reducer is selected as the speed reducers of the upper part and the lower part of the mechanism.

Checking the shaft strength of the pressing screw rod: the power of the selected motor is 4kW, and the minimum diameter of the estimated feeding area of the pressing screw rod is d ₁ Checking the selected parameters when the selected parameters are 60 mm.

In the formula (26), P is the rated power of the motor;

n-screw rotation speed.

The material of the shaft is 45 steel for reference data, and A is obtained by looking up the table ₀ 110, data is substituted into formula (26) to obtain:

the minimum diameter of the feeding area of the pressing screw rod is selected as d ₁ 60mm satisfies the strength. The minimum diameter d of the output shaft of the screw rod is 36mm, the strength is enough, and the shaft section with the minimum diameter is connected with the coupling.

Parameter design of the intermittent mechanism: in order to realize the start and stop of the rotation of the octagonal roller, the parameter design of the intermittent mechanism is needed, fig. 18 is a plan view of the intermittent mechanism, and in the plan view, 1 is a crank round pin 2, 3 is a disc (a), 4 is a disc (b), 5 is a shifting pin tooth, 6 is a roller connecting disc, and 7 is a roller round pin.

1. Selection of number of round pins of intermittent mechanism

As can be seen from fig. 22, the drum has an octagonal shape, and the angle of rotation of the octagonal drum for each station is 45 degrees, so that the number of round pins of the disc (c) is also 8 and the angle interval between every two round pins is also 45 degrees in order to better correspond to the rotation of the stations.

2. Time distribution and angle interval of crank round pin and pulling pin tooth

The crank round pin is a fulcrum for providing reciprocating motion power for the denucleation needle plate. The crank round pin is connected with the denucleation needle plate through a crank, and the motion principle of a crank sliding block is adopted. The poking pin teeth are in mutual contact with the round pin of the roller, the poking pin teeth transmit a rotating force to the round pin of the roller under the rotation of the disc (b), the disc (c) can rotate a station at the moment, and the octagonal roller also rotates a station along with the rotation of the disc (c). In order to enable the coring needle to complete the coring action within the time of the octagonal roller being idle, a movement time distribution and an angular interval calculation are performed between the crank round pin and the pin pulling tooth.

As can be seen from the foregoing, the coring needle makes 30 times of up-and-down reciprocating motions per minute, since the time for a single up-and-down reciprocating motion of the coring needle is 2s, and the rotation speed of the motor is equal to 30 r/min.

The movement between the crank round pin and the pin pulling tooth is shown in fig. 19:

it can be seen from figure 19 that when the dog teeth start to rotate from position 2 to 2', the drum has now rotated from the inclined first station to the second horizontal station, which is the station for the coring process, after which the drum is not rotated until the dog teeth again come into contact with the drum pins. From position 2 to position 2', turning 45 degrees, the time spent is:

in formula (28), t ₁ -time of position 2 to position 2';

-the angle turned from position 2 to position 2';

t is the time for the coring needle to reciprocate, and T is 2 s.

Substituting data into formula (28)

After the pin pulling teeth rotate for 0.25s, the roller is still, and the processing plane is kept horizontal. At this time, the position of the crankpin is changed from 1 to 1 ', and after 1' reaches 1 ″, the coring needle plate moves downward to the lowermost end. When the cherry pit is removed to the lowest point, the process of pit removal is also completed, and the time consumed for pit removal is negligible. Position 1' to position 1 ", the elapsed time is:

in the formula (30), t ₂ -time of location 1 to location 1';

-the angle turned by position 1 to position 1';

t is the time for the coring needle to reciprocate, and T is 2 s.

Substituting data into formula (30)

The process of stoning the cherries is completed when the crank round pin goes from the position 1 'to the position 1', so that the time consumed by the cutter to eject the pit is negligible.

After the denucleation needle completes denucleation at the position 1 ', the disc (b) continues to rotate, and after the position 1' returns to the position 1, the time for the process is as follows:

in the formula (30), t ₃ -time of position 1' to position 1 ";

-the angle turned by position 1' to position 1 ";

t is the time for the coring needle to reciprocate, and T is 2 s.

Substituting data into formula (32)

The overall exercise time consumption is:

t＝t ₁ +t ₂ +t ₃ ＝0.25+0.5+1.25＝2s (34)

the total time is exactly equal to the time 2s taken for the coring needle to reciprocate.

After 315 degrees of rotation of the crankpin, i.e. after 1.75 seconds, the coring needle is at the highest point. After rotating 360 degrees, the above-mentioned rotation action is returned, and the next denucleation processing is not started until the round pin tooth is contacted with the next roller round pin.

In conclusion, when the angle interval between the crank round pin and the pin pulling tooth is 135 degrees, the motion fit between the coring needle and the roller can be just met.

Checking and calculating the stress and strength of the poking pin teeth: in order to better check the strength of the shift pin teeth and whether the provided power can provide enough power for the roller, the power and strength of the shift pin teeth need to be checked and calculated, and a cylindrical gear method is adopted for checking and calculating.

1) Force calculation

As can be seen from the foregoing, the output of the motor is 3kW, the rotational speed is 30r/min, and the pin pulling teeth are subjected to stress decomposition, as shown in FIG. 20.

Calculated from the torque equation:

substituting data into an equation (35) to obtain:

then F _t Comprises the following steps:

in equation (37), d represents the minimum diameter of the dial, and d is 40 mm. Substituting the data to obtain:

so that F can be calculated _n Obtaining:

the torque provided to the dog teeth is:

T _tooth ＝F _n ·l (40)

In the formula (40), l is the distance from the circle center of the driving plate to the tangent point of the pin tooth and the round pin. Taking l as 43mm, and substituting data into an equation (40) to obtain:

T _tooth ＝F _n ·l＝51684.2×43×10 ^-3 ＝2222.42N·m (41)

At the roller, it can be seen from the foregoing that the total weight of the entire feeding system is estimated to be 1500N, and further, the total weight is estimated to be 1700N in consideration of the influence due to the frictional force. Thus, the torque to rotate the drum can be calculated as:

T _cartridge ＝F _Cartridge ·r (42)

In the formula (42), r is the radius of the roller, and r is approximately equal to 200 mm. Substituting data into an equation (42) to obtain:

T _cartridge ＝F _Cartridge ·r＝1700×200×10 ^-3 ＝340N·m (43)

As can be seen from the calculation results, the torque provided by the pin pulling teeth is 6.5 times of the torque required by the roller, so that the torque provided by the pin pulling teeth can drive the roller to rotate.

2) Calculation of strength of shift teeth

The strength of the pin pulling tooth can be calculated according to the tooth root bending fatigue strength of the cylindrical gear, the tooth width b of the tooth is 20mm, the tooth number z is 17, and the modulus m is 12. The bending stress to which the pin tooth is subjected is calculated by the formula as follows:

in the formula (44), Y _Fa Coefficient of tooth form, taking Y _Fa 2.97. Substituting the data into an equation (44) to obtain:

adding a correction coefficient and a load coefficient, the bending fatigue strength is as follows:

σ _F ＝σ _F0 K _F Y _Sa Y _e ≤[σ _F ] (46)

in formula (46), K _F Calculated load factor of bending fatigue strength, K _F ＝1.4；

Y _Sa Stress correction factor, taking Y _Sa ＝1.52；

Y _e -contact ratio coefficient of bending fatigue strength calculation, taking Y _e ＝0.688

[σ _F ]Root bending fatigue limit, taking [ sigma ] _F ]＝500MPa。

Substituting the data into an equation (46) to obtain:

in conclusion, the pin pulling tooth can meet the strength requirement.

The control method of the cherry denucleating and pulping device comprises the following steps: as shown in fig. 21, when the start button is pressed, the motor M1 (the driving motor of the pitter mechanism) starts to start, the feeding of cherries is started, the roller is rotated by the power transmitted by the intermittent mechanism to convey the cherries, and the motor of the beating mechanism is not started. When the octagonal roller mechanism rotates five sides, namely the denucleation mechanism completes five denucleation actions, namely 10s, the motor M2 of the beating mechanism starts to complete the beating action. When the placing groove on the roller is found to be not provided with cherries, the stop button is pressed, and in order to prevent the feed hopper from remaining with cherries on the fruit blocking plate, the motor M1 needs to be stopped after delaying for 10s after the stop button is pressed. Considering that there are remaining cherries that have not been squeezed in time, the motor M2 needs to be turned off with a delay after the stop button is pressed. As known from section 4.2.3, the moving speed of the beating mechanism is 0.1M/s, the total length of the squeezing spiral rod is about 800mm, and considering that the beating mechanism can squeeze the rest cherries more completely, after a stop button is pressed, the motor M2 needs to be delayed for 20s and then stopped.

According to the control requirement of the device, as shown in fig. 21, the control operation principle of the motor is as follows:

1) before the starting, the circuit is in an initial state, the coils of the contactors KM1, KM2, KT1, KT2 and KT3 are in a power-off state, and the motor is not electrified but stands still;

2) closing the switch QG to introduce power into the circuit;

3) when a motor starting button SB1 is pressed, a coil KM1 is firstly electrified and then self-locked, a KM1 contactor is closed, a motor M1 starts to operate, and a coil KT1 starts to be electrified;

4) when the electrifying delay time (10s) of the coil KT1 reaches the closing time of the rear movable contact KT1, the KM2 coil is self-locked after being electrified, the KM2 contactor is closed, and the motor M2 starts to run;

5) when the motor stops working, a stop button SB3 is pressed first, coils KT2 and KT3 start to be electrified, when the power-off delay time (10s) of the coil KT3 is up, a dynamic break contact KT3 is disconnected, a coil KM1 is powered off, the motor M1 stops running, when the power-off delay time (20s) of the coil KT2 is up, the dynamic break contact KT2 is disconnected, a coil KM2 is powered off, and the motor M2 stops running;

6) when the two motors are required to be completely stopped, the emergency button SB2 is required to be pressed;

7) adopt fuse FU to realize short-circuit protection, adopt relay KH to realize overload protection.

The cherry stone removing and beating device has the following advantages:

(1) the utility model provides a collect cherry denucleate and making beating device as an organic whole, the device structural partitioning is clear, and the mechanism of denucleating is last, and the making beating mechanism is under, and overall structure is compact, has not only solved the problem that shifts the cherry making beating and consume strength consuming time, has guaranteed in addition that the cherry pit is not taken place by the condition of smashing. The device is characterized in that during the operation process, the cherry is denucleated by the denucleation mechanism, and then the denucleated cherry directly enters the pulping mechanism for pulping, the two mechanisms are not interfered with each other during the working process, so that the requirement of integration of denucleation and pulping is met, the working efficiency is improved, and the cherry processing process is more modern; the device can avoid the transfer of cherries after the denucleation is finished, and immediately pulp after the denucleation is finished, thereby preventing the deterioration of the cherries from affecting the taste of the fruit wine;

(2) a barrel rod type coring mode is adopted, the coring mechanism is connected with a crank sliding block to realize the up-and-down reciprocating motion of the coring mechanism, and cherry stones are ejected out by utilizing downward inertia;

(3) the feeding device adopts an octagonal roller to carry out rotary feeding, after a whole plane of roller feeding reaches a vertical top position during working, a denucleation mechanism denucleates cherries, and after denucleation is finished, the denucleated cherries fall to a pulping mechanism for pulping after the roller rotates, the denucleates the cherries, the denucleates and the pulping mechanism do not interfere with each other in the working process of the two mechanisms, the integral requirement of denucleation and pulping is met, the octagonal roller is provided with eight uniformly distributed planes, multiple rows of denucleates can be generated at one time, the efficiency is greatly improved, the roller is of a plane structure, the stress is balanced, overturning is avoided, and the denucleation stability is better;

(4) the cutter guide plate is arranged, so that directional coring and precise coring can be realized, the stability of the end part of the cutter is provided, the rigidity is prevented from weakening after the cutter is blocked by kernels, the coring effect is better, and the cutter guide plate can also play a role in preventing displacement of cherries in the cutter withdrawing process;

(5) the segmented cutter structure can more quickly cut peel in the process of denucleating and timely eject out the kernels, so that the efficiency of denucleating the kernels is higher;

(6) the intermittent driving mechanism formed by the crank disc, the connecting rod, the gear shifting disc and the sheave plate can drive the denucleation mechanism to denucleate while realizing the rotation of an octahedral feeding roller, so that the cost is greatly reduced, only one power source is needed to realize, the cost is greatly reduced, the intermittent mechanism has the characteristics of simple structure, high mechanical efficiency and the like, can stably and intermittently rotate in the working process, and meets the requirements of rotation and intermittent stop of the octagonal roller;

(7) the two ends of the feeding roller are provided with circular guide rails which are matched with arc-shaped guide blocks on the feeding hopper and are matched with the two pairs of supporting wheels, so that the feeding roller has the function of directional rotation on one hand and has the function of anti-overturning in the rotating process of the feeding roller on the other hand;

(8) the cherry stone removing device is provided with a plurality of staggered rows of rollers for limiting the flowing speed of cherries, and an elastic telescopic baffle plate for preventing the cherries for removing stones from falling to a pulping mechanism from a gap between the roller and a hopper;

(9) the making beating device adopts spiral juice extractor then, and spiral juice extractor can accomplish the back of denucleating at the stoner, can carry out rapid juice to the cherry, reaches the purpose of starching.

The above description is only for the specific embodiments of the present invention, but the protection scope of the present invention is not limited thereto, and any person skilled in the art can easily think of the changes or substitutions within the technical scope of the present invention, and all should be covered within the protection scope of the present invention, therefore, the protection scope of the present invention should be subject to the protection scope of the claims.

Claims (3)

1. The utility model provides a feeder hopper that is used for cherry beating device that denucleates which characterized in that: including strip chamber (201) and roller (202), strip chamber (201) is along box (1) length direction denucleates and be the contained angle with vertical direction and arrange and inside and outside end is open structure, and strip chamber (201) perpendicular to length direction staggers arranges the rotatable roller (202) of multirow, and strip chamber (201) length direction bottom curb plate is provided with elastic telescopic baffle (203), and elastic telescopic baffle (203) support and lean on in loading roller (302) length direction.

2. The feed hopper for the cherry stone-removing beating device of claim 1, characterized in that: still including this feeder hopper (2) both ends inboard setting two arc guide block (322), the arc guide way internalization of two arc guide block (322) is embedded with two ring guide rail (321) that set up on the loading cylinder and the outer cylinder of two ring guide rail (321) and the medial surface of arc guide way keep the clearance, and two arc guide block (322) set up on the both ends lateral wall of feeder hopper (2).

3. The feeding hopper for the cherry stone-removing beating device as claimed in claim 1, wherein: the elastic telescopic baffle (203) is movably embedded into a strip-shaped blind hole (205) on the side plate, the inner end of the elastic telescopic baffle is connected with a spring (204), and the inner end of the spring (204) is connected to the bottom of the strip-shaped blind hole.

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