Novel cold state presser with low dry cake residual oil rate and barrel cooling method

Abstract

A pressing cage of the presser comprises a plurality of cage containing plates, heat exchange channels are formed in the inner walls of inner holes of the cage containing plates, and a plurality of pressing strips are arranged on the side walls of the heat exchange channels; the root diameter of a squeezing section of a spiral shaft of the squeezer is gradually increased in the direction close to a cake outlet end in the axial direction, the tooth face screw pitch and the tooth back screw pitch of spiral squeezing teeth are two unequal screw pitches, the tooth face screw pitch is larger than the tooth back screw pitch, and the spiral groove width and the spiral groove depth of the spiral shaft are gradually decreased in the direction close to the cake outlet end in the axial direction. And a cooling water cavity is formed in the spiral shaft. By designing the pressing cage water-cooling structure and the spiral shaft water-cooling structure, the pressing temperature in the barrel is greatly reduced; the spiral shaft adopts a tooth surface and tooth back double-screw-pitch design, and is matched with a cone-frustum-shaped tooth root circle, so that the retaining amount of pressed oil in the barrel is reduced, the unit pressure of the pressed oil in the barrel is greatly improved, and the residual oil rate of a dry cake is reduced while the oil outlet quality and the oil outlet efficiency are improved.

Description

Technical Field

[0001] The invention relates to the technical field of screw oil presses, and in particular to a novel cold press with low dry cake residual oil rate and a pressing chamber cooling method. Background Art

[0002] The low-temperature cold pressing process of oil is a new pressing process developed at the end of the last century and the beginning of this century. Different from the traditional high-temperature hot pressing process of the screw oil press, the low-temperature cold pressing machine must have a pressing temperature of less than 65°C during the entire pressing process from the feeding into the pressing to the separation of the pressed cake from the pressing chamber. Therefore, the low-temperature cold pressing process has the characteristics of fully retaining various nutrients, good quality of cold-pressed oil, small protein denaturation of cold-pressed cakes, high comprehensive utilization and development value, and green environmental protection and pollution-free. Therefore, the research and development of low-temperature cold pressing machines has received extensive attention and participation from scientific and technological workers at home and abroad. For example, the twin-screw oil press developed in my country came into being in the upsurge of low-temperature cold pressing machine research and development. Unfortunately, this model does not adopt any cooling design, and its pressing temperature in the pressing chamber is still as high as 90°C, which is far from the process design requirements of low-temperature cold pressing machines. The Kp series low-temperature cold press developed and manufactured by Germany's Kemreia-SKET company, although the pressing temperature of the pressing chamber meets the requirements of the low-temperature cold pressing process, the dry cake residual oil rate of the cold-pressed cake is as high as 10% to 14%. Compared with the 6% to 7% dry cake residual oil rate of the traditional high-temperature hot pressing process, its oil output efficiency is low and the oil loss is too large. If secondary pressing is adopted, the processing cost will increase, and the degree of protein denaturation in the pressed cake will also increase, reducing the development and utilization value of the protein in the pressed cake.

[0003] The reasons why the Kp series low-temperature cold press is not satisfactory mainly include the following aspects:

[0004] First, the cooling measures for the press chamber are single and the cooling effect is not adequate;

[0005] Secondly, it only adopts the hollow shaft water injection cooling design for the transmission main shaft of the traditional screw oil press, but does not take into account the cooling of the transmission main shaft and then indirectly cooling the spiral parts (such as the combined pressing parts such as the pressing screw, liner and smooth sleeve) on it. The total cooling wall thickness is too large. The wall thickness of the hollow transmission main shaft + the wall thickness of the combined pressing parts of the pressing screw is at least between 50mm and 60mm. The larger the machine model, the larger the wall thickness that needs to be cooled, and the worse the cooling effect. Therefore, the Kp series low-temperature cold press has reduced and controlled the design of the pressing chamber pressure. The pressing chamber pressure is proportional to the pressing chamber temperature and inversely proportional to the dry cake residual oil rate of the cold-pressed cake. It is this "low pressure, low temperature" design of the pressing chamber that leads to the excessively high residual oil rate and excessive oil loss of its cold-pressed biscuits.

[0006] Thirdly, its screw shaft still adopts the conventional method of ordinary screw oil press, which is composed of multi-section pressing screws, multiple bushings and other pressing parts connected with the transmission main shaft through the inner hole key connection, resulting in too many calculated spiral turns in the pressing chamber and too much corresponding pressed oil in the pressing chamber, making the unit pressure of the pressed oil in the pressing chamber too low. The insufficient unit pressure will inevitably increase the dry cake residual oil rate and oil loss, and seriously affect the oil output efficiency of the low-temperature cold press.

[0007] In summary, how to improve the current "low pressure, low temperature" working conditions to "high pressure, low temperature" working conditions, while ensuring the quality of oil output, to improve the oil output efficiency as much as possible and reduce the dry cake residual oil rate, the design and development of the pressing cage, spiral shaft cooling design and spiral pressing teeth have become the key to solving the problem. Summary of the invention

[0008] The present invention proposes a novel cold press with low dry cake residual oil rate and a pressing chamber cooling method, which solves the problem that the cold press in the prior art cannot take into account the "high pressure, low temperature" working environment, resulting in the inability to simultaneously ensure high oil quality, high oil efficiency and low dry cake residual oil rate.

[0009] The technical solution of the present invention is achieved in this way:

[0010] The first aspect of the present invention provides a novel cold press with low dry cake residual oil rate, comprising a frame, a controller, a driving component and a pressing cage are installed on the frame, a feeding hopper is installed at the feed end of the pressing cage, and a single screw shaft or multiple screw shafts are installed in the pressing cage;

[0011] The pressing cage comprises a plurality of cage plates arranged at intervals along the axial direction, and the opposite side edges of the plurality of cage plates are fixedly connected by a first connecting plate and a second connecting plate respectively; a heat exchange channel is provided on the inner wall of the inner hole of the cage plate along the circumferential direction, and a plurality of pressing bars are arranged adjacent to the side wall of the heat exchange channel along the circumferential direction, and the plurality of pressing bars are surrounded to form a pressing chamber; the heat exchange channel is connected to the external circulation pipeline through a corresponding flow channel;

[0012] The spiral shaft comprises a feeding section spiral shaft and a pressing section spiral shaft, the root circle diameter of the pressing section spiral shaft gradually increases along the axial direction close to the cake outlet end, the tooth surface pitch S1 and the tooth back pitch S2 of the spiral pressing teeth of the pressing section spiral shaft are two unequal pitches, and the tooth surface pitch S1 is greater than the tooth back pitch S2, and the spiral groove width and spiral groove depth of the pressing section spiral shaft gradually decrease along the axial direction close to the cake outlet end;

[0013] A cooling water chamber is provided inside the spiral shaft, and the cooling water chamber is communicated with an external first water inlet pipe and a first water outlet pipe.

[0014] Optionally, the heat exchange channel includes a cooling water tank, a heat exchange tube is embedded in the cooling water tank, a plurality of the pressing strips are arranged closely along the circumference of the side wall of the heat exchange tube, and the heat exchange tube is connected to the external circulation pipeline through a corresponding flow channel.

[0015] Preferably, the heat exchange channel comprises a cooling water trough, a sealing sleeve is welded on the opening side of the cooling water trough, a plurality of the pressing strips are arranged closely along the circumference of the side wall of the sealing sleeve, and the cooling water trough is connected to the external circulation pipeline through a corresponding flow channel.

[0016] Preferably, the external circulation pipeline includes a shunt pipe and a water collecting pipe, and the shunt pipe and the water collecting pipe are respectively installed on the first connecting plate and the second connecting plate; the shunt pipe is connected with the heat exchange channel of each caged plate through the corresponding first flow channel, and the water collecting pipe is connected with the heat exchange channel of each caged plate through the corresponding second flow channel, and the shunt pipe and the water collecting pipe are respectively connected with the second water inlet pipe and the second water outlet pipe; low-temperature coolant is introduced into the shunt pipe through the second water inlet pipe, and the coolant is diverted by the shunt pipe and enters the heat exchange channel with the first flow channel of each caged plate to exchange heat with the pressing bars in the pressing chamber, and then is collected into the water collecting pipe through the second flow channel of each caged plate, and finally is discharged from the second water outlet pipe. By connecting the circulation pipelines of the heat exchange channels of multiple caged plates in parallel, the pipeline layout cost can be saved, the pipeline layout space can be reduced, and on-site installation and use are convenient.

[0017] Optionally, the external circulation pipeline includes several groups of independent second water inlet pipes and second water outlet pipes, and each group of the second water inlet pipes and the second water outlet pipes are respectively connected to the heat exchange channels of the corresponding caged plates through the first flow channel and the second flow channel; by independently setting the circulation pipelines of the heat exchange channels of each caged plate, the medium temperature, flow rate and other parameters of each circulation pipeline can be independently adjusted to accurately control the temperature of different parts in the pressing chamber.

[0018] Optionally, the cage plate is composed of two semi-annular plates, and the two semi-annular plates are detachably connected via a connecting piece. This detachable cage plate structure is more suitable for installation in large and medium-sized machines.

[0019] Specifically, a pressure plate is fixedly installed at both ends of the inner hole of each semi-annular plate, and several pressing strips are arranged closely between the two pressing plates. Through the pressure plates at both ends, several pressing strips can be tightly pressed onto the inner wall of the sealing sleeve corresponding to the inner hole of the semi-annular plate.

[0020] Furthermore, the heat exchange channel and the sealing sleeve are both two-section split structures, and both end openings of the heat exchange channel are provided with sealing plugs; the first connecting plate, the second connecting plate, the diverter pipe, the water collecting pipe, the first flow channel, and the second flow channel are each provided with two groups, which are respectively used for circulating water through the heat exchange channels inside the two semi-annular plates; since pressure plates are installed at both ends of the inner holes of the semi-annular plates, the original integral annular heat exchange channel and the sealing sleeve are separated into two independent structures by the pressure plates. Therefore, by setting two groups of independent circulation pipelines, coolant is respectively introduced into the heat exchange channels in the two semi-annular plates to realize circulating cooling of the split cage plate.

[0021] Specifically, the connecting parts include bolts, pins and ear plates, and the sides of the two first connecting plates and the second connecting plates are provided with through holes for installing bolts; ear plates are respectively installed at both ends of the bottom surfaces of the two second connecting plates, and the pins pass through the axial holes of the four ear plates in sequence; the two second connecting plates at the bottom ends of the two semi-annular plates are hinged by ear plates and pins, so as to facilitate automatic alignment of the two semi-annular plates when closed, and the two first connecting plates at the upper part of the two semi-annular plates are locked by bolts, and the two second connecting plates at the lower part of the two semi-annular plates are locked by bolts to achieve locking and fixation of the two semi-annular plates.

[0022] Furthermore, a notch is provided at the position where the water collecting pipe passes through the ear plate, and the notch is seal-welded to the ear plate, so as to avoid the ear plate affecting the layout path of the water collecting pipe without affecting the sealing of the water collecting pipe.

[0023] Furthermore, the bolt is installed at a position between two adjacent cage plates on the first connecting plate and between two adjacent cage plates on the second connecting plate, and the penetration path of the bolt is staggered with the first flow channel in the first connecting plate and the second flow channel in the second connecting plate, thereby avoiding the influence of the installation of the bolt on the first flow channel and the second flow channel.

[0024] Preferably, the width of the spiral teeth increases gradually along the axial direction close to the cake outlet end. The purpose of such design is to shorten the axial length of the spiral teeth and the total number of spiral circles as much as possible, so as to ensure that under the conditions of unchanged oil input, unchanged input power, unchanged screw shaft speed and unchanged total compression ratio, on the one hand, the unit pressure of the squeezed oil in the pressing chamber is increased, and the oil output efficiency is improved; on the other hand, the pressing time of the oil in the pressing chamber can be shortened, thereby reducing the pressing temperature and improving the oil output quality.

[0025] Specifically, the difference between the width at the beginning and the width at the end of any circle of the spiral groove is Δl=S1-S2.

[0026] Specifically, the length of the spiral shaft of the pressing section L=S2×n+b2, wherein n represents the number of spiral pressing tooth turns, and b2 represents the axial width of the end of the spiral pressing tooth.

[0027] Specifically, the end width of the spiral groove l=S2×n-b1-S1×(n-1), wherein n represents the number of spiral pressing tooth turns, and b1 represents the axial width of the starting end of the spiral pressing tooth.

[0028] Specifically, the two ends of the spiral shaft are respectively connected with a power input shaft and a rotating support shaft, the spiral pressing teeth are integrally formed with the spiral shaft; the rotating support shaft is a hollow shaft, and the shaft hole of the rotating support shaft is connected with the cooling water cavity, and the first water inlet pipe and the first water outlet pipe are installed at the end of the rotating support shaft. By setting a cooling water cavity inside the spiral shaft and passing a cooling medium into the cooling water cavity through the shaft hole of the rotating support shaft, the spiral shaft can be quickly cooled.

[0029] Furthermore, a bearing assembly is installed on the outside of the rotating support shaft, and a cover shell is seal-mounted on the outer end face of the bearing assembly; one end of the first water inlet pipe is located outside the cover shell, and the other end is located inside the cover shell and extends to the inside of the cooling water chamber, and the first water outlet pipe is installed on the outside of the bottom of the cover shell; by sealingly installing the cover shell on the outer end face of the bearing assembly, and installing the first water inlet pipe and the first water outlet pipe on the cover shell, the external low-temperature cooling medium can be introduced into the cooling water chamber through the first water inlet pipe to exchange heat with the spiral shaft, and the cooling medium after heat exchange can be discharged into the cover shell through the shaft hole of the rotating support shaft, and finally discharged through the first water outlet pipe at the bottom of the cover shell, thereby realizing circulating cooling of the spiral shaft.

[0030] Furthermore, the bearing assembly includes a bearing sleeve fixedly mounted on the outside of a rotating support shaft, the outer sleeve of the bearing sleeve is provided with a roller bearing, the outer sleeve of the roller bearing is provided with a bearing seat, the front and rear ends of the bearing seat are provided with bearing covers, the open end of the cover shell is sealed and welded to the bearing cover at the front end of the bearing seat, and an oil seal element is provided between the inner side of the bearing cover and the bearing sleeve; through the mutual cooperation of the bearing sleeve, roller bearing, bearing seat, bearing cover and oil seal element, the sealing of the bearing assembly can be ensured to prevent the cooling medium from penetrating into the interior of the bearing assembly or extending out of the cover shell.

[0031] Furthermore, the roller bearing is a spherical roller bearing, and an adjusting nut is provided at the front end of the spherical roller bearing. The adjusting nut is used to adjust the axial clearance of the roller bearing to ensure the stability of the rotation of the rotating support shaft.

[0032] Furthermore, a mounting hole is provided on the side of the cover shell, a threaded joint is sealed and installed in the mounting hole, and the first water inlet pipe is fixedly installed on the cover shell through the threaded joint.

[0033] Specifically, threaded holes are provided at both ends of the screw shaft, and the thread rotation direction of the threaded holes is opposite to that of the screw shaft, and the power input shaft, the rotation support shaft and the screw shaft are connected by threads; by threading the screw shaft with the power input shaft and the rotation support shaft at both ends, the processing and assembly of the screw shaft are facilitated, and the power input shaft, the screw shaft and the rotation support shaft can be processed separately.

[0034] Furthermore, both end faces of the screw shaft are provided with annular grooves, and sealing rings are embedded in the annular grooves, which can improve the sealing performance of the connection between the screw shaft and the power input shaft and the rotating support shaft.

[0035] Specifically, the root circle diameter of the spiral shaft of the feeding section is constant, and the cooling water chamber is opened inside the spiral shaft of the pressing section; since the volume between the pressing chamber and the spiral shaft of the feeding section is fixed, less heat is generated; while in the pressing section, since the root circle diameter of the spiral shaft of the pressing section gradually increases, the volume between the pressing chamber and the spiral shaft of the pressing section gradually decreases, and more heat is generated. Therefore, it is only necessary to open a cooling water chamber inside the spiral shaft of the pressing section for cooling.

[0036] A second aspect of the present invention provides a method for cooling a pressing chamber, comprising the following steps:

[0037] Real-time monitoring of operating temperature data in the pressing chamber;

[0038] According to the monitored temperature data, the external circulation pipeline is controlled to circulate the cooling medium into the heat exchange channel of the cage plate, and the first water inlet pipe and the first water outlet pipe are controlled to circulate the cooling medium into the cooling water cavity inside the spiral shaft;

[0039] The higher the operating temperature in the press chamber, the greater the flow rate and faster the flow rate of the cooling medium circulation.

[0040] Compared with the prior art, the beneficial effects of the present invention are:

[0041] (1) The present invention provides a heat exchange channel on the inner wall of the inner hole of the cage plate. When working, a cooling liquid is circulated into the heat exchange channel through an external circulation pipeline. The heat on the pressing bar is transferred to the heat exchange channel and then taken away by the cooling liquid, thereby quickly reducing the pressing temperature in the pressing chamber, realizing the design concept of "low temperature and high pressure" in the pressing chamber, and realizing low-temperature pressing in the true sense. Under the premise of ensuring the quality of the oil and low denaturation of protein in the cake, the oil output efficiency is maximized;

[0042] (2) The present invention improves the pressing section of the traditional spiral shaft. The present invention adopts a double pitch design of the tooth surface and the tooth back, and cooperates with a truncated cone tooth root circle. The purpose of this design is: on the one hand, the feeding end of the spiral groove is wide and deep, and the cake outlet end is narrow and shallow. During the movement of the oil from the beginning to the end of the spiral groove, every moment is continuously subjected to the double squeezing effect of the spiral groove narrowing and shallowing; on the other hand, the number of spiral calculation circles in the pressing chamber is reduced, and the amount of squeezed oil in the pressing chamber is correspondingly reduced, so that the unit pressure of the squeezed oil in the pressing chamber is greatly improved. This advantage of the present invention can improve the oil output efficiency of the low-temperature cold press and reduce oil loss;

[0043] (3) Since the conventional screw shaft is composed of a number of pressing screws, bushings, and smooth sleeves, and rotates with the transmission main shaft through an inner hole key connection, when the screw shaft is cooled, its cooling thickness includes the thickness of the pressing screw + the wall thickness of the transmission main shaft, and the cooling effect is poor; the present invention adopts a truncated cone-shaped screw shaft to replace the original transmission main shaft functional design, and changes the indirect cooling screw shaft of the transmission main shaft to a direct cooling screw shaft, which not only reduces the cooling wall thickness of the transmission main shaft, but also increases the cross-sectional area of ​​the cooling water cavity, greatly improving the cooling effect of the screw shaft, thereby maintaining a low pressing temperature without sacrificing the pressing chamber pressure, realizing true high-pressure and low-temperature pressing, reducing the dry cake residual oil rate, and improving the oil output efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0045] Figure 1 It is a schematic diagram of the overall structure of a new type of cold press with low dry cake residual oil rate according to the present invention;

[0046] Figure 2 It is a schematic diagram of the internal structure of the integrated cage plate in an embodiment of the present invention;

[0047] Figure 3 It is a schematic diagram of the internal structure of the split cage plate in an embodiment of the present invention;

[0048] Figure 4 It is a schematic diagram of the structure after the split cage plate is opened in the embodiment of the present invention;

[0049] Figure 5 This is a front view of a pressing cage in an embodiment of the present invention;

[0050] Figure 6A top view of a pressing cage in an embodiment of the present invention;

[0051] Figure 7 A bottom view of a pressing cage in an embodiment of the present invention;

[0052] Figure 8 Schematic diagram of the structure of the spiral shaft of the pressing section in an embodiment of the present invention;

[0053] Fig. 9 Schematic diagram of the internal structure of the spiral shaft in an embodiment of the present invention;

[0054] Fig.10 for Fig. 9 Enlarged view of part A in the middle;

[0055] Fig.11 Schematic diagram of the external structure of the spiral shaft in an embodiment of the present invention;

[0056] Fig.12 The dry cake morphology diagram corresponding to the four groups of test data in the embodiment of the present invention;

[0057] In the figure: 1, frame; 2, controller; 3, driving component; 4, pressing cage; 5, feeding hopper; 6, cage plate; 7, first connecting plate; 8, second connecting plate; 9, cooling water tank; 10, sealing sleeve; 11, pressing bar; 12, shunt pipe; 13, water collecting pipe; 14, first flow channel; 15, second flow channel; 16, second water inlet pipe; 17, second water outlet pipe; 18, semi-circular plate; 19, pressing plate; 20, sealing plug; 21, bolt; 22, pin shaft; 23, ear plate; 24, notch; 2 5. Spiral pressing teeth; 26. Feeding section spiral shaft; 27. Pressing section spiral shaft; 28. Spiral groove; 29. ​​Tooth surface; 30. Tooth back; 31. Cooling water chamber; 32. First water inlet pipe; 33. First water outlet pipe; 34. Power input shaft; 35. Rotary support shaft; 36. Shaft hole; 37. Cover; 38. Bearing sleeve; 39. Roller bearing; 40. Bearing seat; 41. Bearing cover; 42. Oil seal element; 43. Adjusting nut; 44. Threaded joint; 45. Threaded hole; 46. Sealing ring. DETAILED DESCRIPTION

[0058] The technical solution of the present invention will be clearly and completely described below in conjunction with the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0059] Reference Figures 1 to 11The first aspect of the embodiment of the present invention provides a novel cold press with low dry cake residual oil rate, comprising a frame 1, on which a controller 2, a driving component 3 and a pressing cage 4 are installed, a feeding hopper 5 is installed at the feeding end of the pressing cage 4, and a single screw shaft or multiple screw shafts are installed in the pressing cage 4;

[0060] The pressing cage 4 comprises a plurality of cage plates 6 arranged at intervals along the axial direction, and the opposite side edges of the plurality of cage plates 6 are fixedly connected by a first connecting plate 7 and a second connecting plate 8 respectively; a heat exchange channel is provided on the inner wall of the inner hole of the cage plate 6 along the circumferential direction, and a plurality of pressing bars 11 are arranged adjacent to the side wall of the heat exchange channel along the circumferential direction, and the plurality of pressing bars 11 are surrounded to form a pressing chamber; the heat exchange channel is connected to the external circulation pipeline through a corresponding flow channel;

[0061] The spiral shaft comprises a feeding section spiral shaft 26 and a pressing section spiral shaft 27, the root circle diameter of the pressing section spiral shaft 27 gradually increases along the axial direction close to the cake outlet end, the pitch S1 of the tooth surface 29 and the pitch S2 of the tooth back 30 of the spiral pressing teeth 25 of the pressing section spiral shaft 27 are two unequal pitches, and the pitch S1 of the tooth surface 29 is greater than the pitch S2 of the tooth back 30, and the width and depth of the spiral groove 28 of the pressing section spiral shaft 27 gradually decrease along the axial direction close to the cake outlet end;

[0062] A cooling water chamber 31 is provided inside the spiral shaft, and the cooling water chamber 31 is communicated with a first water inlet pipe 32 and a first water outlet pipe 33 outside.

[0063] During the specific implementation process, a plurality of temperature sensors are installed on the pressing cage 4, and the temperature sensors can be installed on the cage plate 6 and the pressing bar 11. The temperature of the oil in the pressing bore is indirectly measured by monitoring the temperature of the cage plate 6 and the pressing bar 11. The controller 2 performs circulating water cooling on the pressing cage 4 and the screw shaft according to the monitored temperature data to ensure that the oil is in a low-temperature pressing environment.

[0064] The driving component 3 includes a motor and a reducer. The motor drives the reducer to drive the screw shaft to rotate, and cooperates with the boring machine to realize the transportation and extrusion of the oil.

[0065] Optionally, the heat exchange channel includes a cooling water tank 9, in which a heat exchange tube (not shown) is embedded, and a plurality of the pressing strips 11 are arranged closely along the circumference of the side wall of the heat exchange tube, and the heat exchange tube is connected to the external circulation pipeline through a corresponding flow channel.

[0066] Preferably, if Figure 2 As shown, the heat exchange channel includes a cooling water trough 9, a sealing sleeve 10 is welded on the open side of the cooling water trough 9, a plurality of pressing strips 11 are arranged closely along the circumference of the side wall of the sealing sleeve 10, and the cooling water trough 9 is connected to the external circulation pipeline through the corresponding flow channel.

[0067] In this embodiment, a closed annular heat exchange channel is obtained by opening a cooling water tank 9 on the inner wall of the inner hole of the cage plate 6 and welding a sealing sleeve 10. In the specific implementation process, it is not limited to the method of embedding a heat exchange copper tube in the cooling water tank 9. Cooling liquid can be circulated in the heat exchange copper tube to achieve rapid cooling of the pressing chamber.

[0068] The sealing sleeve 10 in this embodiment is made of a metal material having welding performance similar to that of the cage plate 6, and the thickness of the sealing sleeve 10 is not easy to be too thick (too thick will lead to reduced heat transfer efficiency); the width of the sealing sleeve 10 is greater than the width of the cooling water trough 9, thereby ensuring the welding sealing effect.

[0069] During the specific implementation process, the cooling water tank 9 is not limited to the processing method, and its cross section is not limited to being designed as a semicircular, rectangular or other shapes; the coolant is not limited to using water, cooling oil or other heat-conducting media.

[0070] In this embodiment, cooling water grooves 9 can be set in all cage plates 6 along the entire axial length of the pressing cage 4 to achieve full cooling of the pressing cage 4 along the axial length, and cooling water grooves 9 can also be set in part of the cage plates 6 along the axial length of the pressing cage 4 to achieve local cooling of the pressing cage 4 along the axial length.

[0071] Preferably, if Figures 2 to 4 As shown, the external circulation pipeline includes a shunt pipe 12 and a water collecting pipe 13, and the shunt pipe 12 and the water collecting pipe 13 are respectively installed on the first connecting plate 7 and the second connecting plate 8; the shunt pipe 12 is respectively connected to the cooling water trough 9 of each cage plate 6 through the corresponding first flow channel 14, and the water collecting pipe 13 is respectively connected to the cooling water trough 9 of each cage plate 6 through the corresponding second flow channel 15, and the shunt pipe 12 and the water collecting pipe 13 are respectively connected to the second water inlet pipe 16 and the second water outlet pipe 17; through the first The second water inlet pipe 16 introduces low-temperature coolant into the shunt pipe 12. After being shunted by the shunt pipe 12, the coolant enters the cooling water trough 9 through the first flow channels 14 of each cage plate 6 to exchange heat with the pressing bars 11 in the pressing chamber, and then passes through the second flow channels 15 of each cage plate 6 to be collected into the collecting pipe 13, and finally discharged from the second water outlet pipe 17. By connecting the circulation pipelines of the cooling water troughs 9 of multiple cage plates 6 in parallel, the pipeline layout cost can be saved, the pipeline layout space can be reduced, and on-site installation and use are convenient.

[0072] In this embodiment, Figures 2 to 4As shown, the first connecting plate 7 is located at the upper part of the cage plate 6, and the second connecting plate 8 is located at the lower part of the cage plate 6. The first connecting plate 7 and the second connecting plate 8 can be cast or welded integrally with the cage plate 6. The first flow channel 14 penetrates from the top surface of the first connecting plate 7 to the cooling water trough 9 inside the cage plate 6, and the second flow channel 15 penetrates from the bottom surface of the second connecting plate 8 to the cooling water trough 9 inside the cage plate 6.

[0073] Furthermore, in this embodiment, if Figures 2 to 4 As shown, the cross-sections of the diverter pipe 12 and the water collecting pipe 13 are semicircular, which can well adapt to the surface shapes of the first connecting plate 7 and the second connecting plate 8; during the specific implementation process, the cross-sectional shapes can also be flexibly selected according to actual conditions.

[0074] In the present embodiment, the diverter pipe 12 and the water collecting pipe 13 are obtained by axially cutting a circular tube from the end face. The side edge of the diverter pipe 12 is sealed and welded to the top surface of the first connecting plate 7 to form a semicircular tube cavity, and the inlets of all the first flow channels 14 on the top surface of the first connecting plate 7 are all connected in parallel in the semicircular tube cavity corresponding to the diverter pipe 12; the side edge of the water collecting pipe 13 is sealed and welded to the bottom surface of the second connecting plate 8 to form a semicircular tube cavity, and the outlets of all the second flow channels 15 on the bottom surface of the second connecting plate 8 are all connected in parallel in the semicircular tube cavity corresponding to the water collecting pipe 13; plugs are welded at both ends of the diverter pipe 12 and the water collecting pipe 13.

[0075] Optionally, the external circulation pipeline includes several groups of independent second water inlet pipes 16 and second water outlet pipes 17, and each group of the second water inlet pipes 16 and the second water outlet pipes 17 are respectively connected to the cooling water trough 9 of the corresponding cage plate 6 through the first flow channel 14 and the second flow channel 15; by independently setting the circulation pipelines of the cooling water troughs 9 of each cage plate 6, the medium temperature, flow rate and other parameters of each circulation pipeline can be independently adjusted to accurately control the temperature of different parts in the pressing chamber.

[0076] Alternatively, if Figure 3 , 4 As shown, the cage plate 6 is composed of two semi-annular plates 18, and the two semi-annular plates 18 are detachably connected by a connecting piece. This detachable cage plate 6 structure is more suitable for the installation of large and medium-sized machines.

[0077] The cage plate 6 of the present embodiment may adopt an integral structure that cannot be opened and closed. When the cage plate 6 is an integral structure, the cooling water groove 9 inside it is a continuous annular groove, and there is no need to use a sealing plug 20; the cage plate 6 of the present embodiment may also adopt an openable and closable split structure. When the cage plate 6 is a split structure, the cooling water groove 9 inside it is two sections of discontinuous semi-annular grooves. If the two ends of the semi-annular groove pass through the open and closed end faces of the semi-annular plate 18, it is necessary to weld sealing plugs 20 at both ends of the semi-annular groove for sealing. If the two ends of the semi-annular groove do not pass through the open and closed end faces of the semi-annular plate 18, there is no need to weld sealing plugs 20 at both ends of the semi-annular groove for sealing.

[0078] Specifically, Figure 3 , 4 As shown, a pressure plate 19 is fixedly installed at both ends of the inner hole of each semi-annular plate 18, and a plurality of pressing strips 11 are arranged closely between the two pressing plates 19. The pressing plates 19 at both ends can tightly press the plurality of pressing strips 11 onto the inner wall of the sealing sleeve 10 corresponding to the inner hole of the semi-annular plate 18.

[0079] Furthermore, if Figure 3 , 4 As shown, the cooling water trough 9 and the sealing sleeve 10 are both two-section split structures, and the openings at both ends of the cooling water trough 9 are provided with sealing plugs 20; the first connecting plate 7, the second connecting plate 8, the diverter pipe 12, the water collecting pipe 13, the first flow channel 14, and the second flow channel 15 are each provided with two groups, which are respectively used for circulating water in the cooling water troughs 9 inside the two semi-annular plates 18; since pressure plates 19 are installed at both ends of the inner hole of the semi-annular plate 18, the original integral annular cooling water trough 9 and the sealing sleeve 10 are separated into two independent structures by the pressure plate 19. Therefore, by setting two groups of independent circulation pipelines, coolant is respectively introduced into the cooling water troughs 9 in the two semi-annular plates 18, so as to realize the circulation cooling of the split cage plate 6.

[0080] Specifically, Figures 3 to 7 As shown, the connecting member includes a bolt 21, a pin 22 and an ear plate 23. The sides of the two first connecting plates 7 and the second connecting plates 8 are provided with through holes for installing the bolts 21; the two ends of the bottom surfaces of the two second connecting plates 8 are respectively installed with ear plates 23, and the pin 22 passes through the axial holes 36 of the four ear plates 23 in sequence; the two second connecting plates 8 at the bottom ends of the two semi-annular plates 18 are hinged by the ear plates 23 and the pin 22, so as to facilitate the automatic alignment of the two semi-annular plates 18 when closed, and the two first connecting plates 7 at the upper part of the two semi-annular plates 18 are locked by the bolts 21, and the two second connecting plates 8 at the lower part of the two semi-annular plates 18 are locked by the bolts 21, so as to realize the locking and fixation of the two semi-annular plates 18.

[0081] Furthermore, if Figure 7As shown, the water collecting pipe 13 is provided with a notch 24 at the position where the ear plate 23 passes, and the notch 24 is sealed and welded to the ear plate 23, so as to avoid the ear plate 23 affecting the layout path of the water collecting pipe 13 without affecting the sealing of the water collecting pipe 13.

[0082] Furthermore, if Figures 5 to 7 As shown, the bolt 21 is installed at a position between two adjacent cage plates 6 on the first connecting plate 7 and between two adjacent cage plates 6 on the second connecting plate 8. The penetration path of the bolt 21 is staggered with the first flow channel 14 in the first connecting plate 7 and the second flow channel 15 in the second connecting plate 8, so as to avoid the influence of the installation of the bolt 21 on the first flow channel 14 and the second flow channel 15.

[0083] During the specific implementation process, the internal structure of the pressing cage 4 of this embodiment can be adaptively adjusted according to the number of spiral shafts to adapt to the cooling of the pressing cage 4 of the multi-spiral cold press; the cooling pressing cage 4 of this embodiment is not limited to being used with a single spiral shaft or a double spiral shaft.

[0084] The water cooling process of the pressing cage 4 in this embodiment is as follows:

[0085] A low-temperature coolant is introduced into the semicircular tube cavity corresponding to the shunt pipe 12 through the second water inlet pipe 16, and the low-temperature coolant is shunted from the shunt pipe 12 into the first flow channel 14 of each cage plate 6, and flows into the cooling water tank 9 of each cage plate 6 from the outlet at the bottom of each first flow channel 14. The coolant exchanges heat with the sealing sleeve 10 in the cooling water tank 9, and quickly takes away the heat generated by the friction between the blank and the pressing bar 11 in the pressing chamber, thereby realizing rapid cooling of the pressing chamber; the coolant after heat exchange is respectively collected from each second flow channel 15 into the semicircular tube cavity corresponding to the water collecting pipe 13, and finally discharged through the second water outlet pipe 17. The discharged coolant is cooled and then introduced into the cooling water tank 9 through the second water inlet pipe 16, thereby realizing water-cooled circulation heat dissipation of the pressing chamber.

[0086] Preferably, if Figure 8 As shown, the width of the spiral teeth 25 gradually increases in the axial direction close to the cake outlet end. The purpose of this design is to ensure that the length and number of turns of the spiral teeth 25 are shortened as much as possible under the conditions of unchanged oil input, unchanged input power, unchanged screw shaft speed, and unchanged total compression ratio. On the one hand, the unit pressure of the squeezed oil in the press chamber is increased, and the oil output efficiency is improved; on the other hand, the pressing time of the oil in the press chamber can be shortened, thereby reducing the pressing temperature and improving the oil output quality.

[0087] Specifically, Figure 8 As shown, the difference between the width at the beginning and the width at the end of any circle of the spiral groove 28 is Δl=S1-S2.

[0088] Specifically, Figure 8As shown, the length L of the screw shaft 27 of the pressing section is S2×n+b2, wherein n represents the number of turns of the screw teeth 25, and b2 represents the axial width of the end of the screw teeth 25.

[0089] Specifically, Figure 8 As shown, the terminal width of the spiral groove 28 is l=S2×n-b1-S1×(n-1), wherein n represents the number of turns of the spiral pressing tooth 25, and b1 represents the axial width of the starting end of the spiral pressing tooth 25.

[0090] Specifically, Fig. 9 As shown, the two ends of the screw shaft are respectively connected with a power input shaft 34 and a rotating support shaft 35, and the spiral pressing teeth 25 are integrally formed with the screw shaft; the rotating support shaft 35 is a hollow shaft, and the shaft hole 36 of the rotating support shaft 35 is connected with the cooling water chamber 31, and the first water inlet pipe 32 and the first water outlet pipe 33 are installed at the end of the rotating support shaft 35. By setting the cooling water chamber 31 inside the screw shaft and passing the cooling medium into the cooling water chamber 31 through the shaft hole 36 of the rotating support shaft 35, the screw shaft can be quickly cooled.

[0091] In this embodiment, the spiral shaft is cut by a CNC lathe, the material of the spiral shaft is 20CrMnTi, the surface is carburized and quenched, the carburized layer depth is 1.5~2mm, and the heat treatment hardness is HRc58~62; the material of the power input shaft 34 is 40Cr, which is tempered and has a hardness of HB260~310; the material of the rotating support shaft 35 is 45# seamless steel pipe, which is tempered and has a hardness of HB190~240.

[0092] Furthermore, if Fig. 9 As shown, a bearing assembly is installed on the outside of the rotating support shaft 35, and a cover 37 is installed on the outer end face of the bearing assembly in a sealed manner; one end of the first water inlet pipe 32 is located outside the cover 37, and the other end is located inside the cover 37 and extends to the inside of the cooling water chamber 31, and the first water outlet pipe 33 is installed on the outside of the bottom of the cover 37; by sealing the cover 37 on the outer end face of the bearing assembly, and installing the first water inlet pipe 32 and the first water outlet pipe 33 on the cover 37, the external low-temperature cooling medium can be introduced into the cooling water chamber 31 through the first water inlet pipe 32 to exchange heat with the spiral shaft, and the cooling medium after heat exchange is discharged into the cover 37 through the shaft hole 36 of the rotating support shaft 35, and finally discharged through the first water outlet pipe 33 at the bottom of the cover 37, thereby realizing cyclic cooling of the spiral shaft. Since the cover 37 is sealed and welded on the outer end face of the bearing assembly, the cover 37 is not affected by the rotation of the spiral shaft.

[0093] During the specific implementation process, in addition to being installed on the bearing assembly through the cover 37, the first water inlet pipe 32 and the first water outlet pipe 33 can also be directly installed on the end of the rotating support shaft 35 with the help of a rotating joint. The structure and installation method of the rotating joint are both conventional means in the field.

[0094] Furthermore, if Fig.10 As shown, the bearing assembly includes a bearing sleeve 38 fixedly sleeved on the outside of the rotating support shaft 35, the outer sleeve of the bearing sleeve 38 is provided with a roller bearing 39, the outer sleeve of the roller bearing 39 is provided with a bearing seat 40, the front and rear ends of the bearing seat 40 are provided with bearing covers 41, the open end of the cover shell 37 is sealed and welded to the bearing cover 41 at the front end of the bearing seat 40, and an oil seal element 42 is provided between the inner side of the bearing cover 41 and the bearing sleeve 38; through the mutual cooperation of the bearing sleeve 38, the roller bearing 39, the bearing seat 40, the bearing cover 41 and the oil seal element 42, the sealing of the bearing assembly can be ensured to prevent the cooling medium from penetrating into the interior of the bearing assembly or extending out of the cover shell 37. During the rotation of the rotating support shaft 35, the bearing sleeve 38 rotates with the rotating support shaft 35, while the bearing seat 40 and the bearing covers 41 at its front and rear ends are fixed. The bearing seat 40 and the bearing sleeve 38 are rotationally connected through the roller bearing 39, and the bearing covers 41 at both ends of the bearing seat 40 cooperate with the oil seal elements 42 to seal the bearing assembly.

[0095] Furthermore, if Fig.10 As shown, the roller bearing 39 is a spherical roller bearing 39 , and an adjusting nut 43 is provided at the front end of the spherical roller bearing 39 . The adjusting nut 43 is used to adjust the axial clearance of the roller bearing 39 to ensure the stability of the rotation of the rotating support shaft 35 .

[0096] Furthermore, if Fig. 9 , 11 As shown, a mounting hole is provided on the side of the cover shell 37 , and a threaded joint 44 is sealed and installed in the mounting hole. The first water inlet pipe 32 is fixedly installed on the cover shell 37 through the threaded joint 44 .

[0097] Specifically, Fig. 9 As shown, threaded holes 45 are provided at both ends of the screw shaft, and the threaded direction of the threaded hole 45 is opposite to that of the screw shaft, and the power input shaft 34 and the rotation support shaft 35 are connected to the screw shaft through threads; by threading the screw shaft to the power input shaft 34 and the rotation support shaft 35 at both ends, the processing and assembly of the screw shaft are facilitated, and the power input shaft 34, the screw shaft and the rotation support shaft 35 can be processed separately.

[0098] Furthermore, if Fig. 9As shown, both end faces of the screw shaft are provided with annular grooves, and sealing rings 46 are embedded in the annular grooves to improve the sealing performance of the connection between the screw shaft and the power input shaft 34 and the rotating support shaft 35.

[0099] Specifically, the root circle diameter of the feeding section spiral shaft 26 is constant, and the cooling water chamber 31 is opened inside the pressing section spiral shaft 27; since the volume between the pressing chamber and the spiral shaft of the feeding section is fixed, less heat is generated; while in the pressing section, since the root circle diameter of the spiral shaft gradually increases, the volume between the pressing chamber and the spiral shaft of the pressing section gradually decreases, and more heat is generated. Therefore, it is only necessary to open a cooling water chamber 31 inside the spiral shaft 27 of the pressing section for cooling.

[0100] Preferably, spiral guide blades (not shown in the figure, similar to the mixing blades provided on the inner wall of a concrete mixing tank) can be provided on the inner wall of the cooling water chamber 31 and the inner wall of the shaft hole 36. On the one hand, the cooling medium in the cooling water chamber 31 can be discharged into the cover shell 37 through the rotation of the spiral guide blades in cooperation with the spiral shaft, thereby improving the circulation efficiency of the cooling medium in the cooling water chamber 31, thereby improving the heat exchange efficiency; on the other hand, the spiral guide blades greatly increase the contact area between the cooling medium and the spiral shaft, thereby further improving the heat exchange efficiency.

[0101] A second aspect of an embodiment of the present invention provides a method for cooling a pressing chamber, comprising the following steps:

[0102] Real-time monitoring of operating temperature data in the pressing chamber;

[0103] According to the monitored temperature data, the external circulation pipeline is controlled to circulate the cooling medium into the heat exchange channel of the cage plate 6, and the first water inlet pipe 32 and the first water outlet pipe 33 are controlled to circulate the cooling medium into the cooling water cavity 31 inside the spiral shaft;

[0104] The higher the operating temperature in the press chamber, the greater the flow rate and faster the flow rate of the cooling medium circulation.

[0105] The water cooling process of the spiral shaft in this embodiment is as follows:

[0106] The screw shaft rotates in the pressing chamber, and is squeezed and rubbed against the blanks in the pressing chamber, generating a large amount of heat. The cooling medium is introduced into the cooling water chamber 31 inside the screw shaft through the first water inlet pipe 32. The cooling medium directly exchanges heat with the screw shaft and absorbs the heat of the screw shaft. As the screw shaft rotates, the cooling medium covers the entire inner wall of the cooling water chamber 31, quickly reducing the temperature of the screw shaft. The cooling medium after heat exchange flows into the cover 37 through the shaft hole 36 of the rotating support shaft 35, and finally flows out from the first water outlet pipe 33 at the bottom of the cover 37, thereby realizing circulating water cooling of the screw shaft.

[0107] When designing the screw shaft of this embodiment, the cross-sectional area between the root circle of the screw shaft and the cooling water chamber can be adjusted to be slightly larger than or equal to the cross-sectional area of ​​the corresponding part of the original transmission shaft. In this way, while ensuring the structural reliability of the screw shaft, the cross-sectional area of ​​the cooling water chamber can be increased as much as possible, thereby maximizing the cooling effect of the screw shaft.

[0108] The screw shaft of the traditional screw oil press is a combination of a transmission shaft and a plurality of screw components with different pitches, several bushings and smooth sleeves connected by keys. Although a cooling design is adopted for the transmission shaft, the wall thickness of the water-passing part of the transmission shaft plus the wall thickness of the assembly parts such as the screw is about 60 mm in total. With such a large thickness, the cooling effect is average. However, since the present invention omits the traditional hollow transmission shaft, the cooling thickness of the screw shaft is reduced by about 50%, and the cooling area of ​​the cooling water is increased, so the cooling effect is significantly improved, which wins a certain space for further increasing the pressing chamber pressure, reducing the residual oil rate of the dry cake, and reducing the oil loss.

[0109] The design process of the spiral shaft in this embodiment is as follows:

[0110] According to the design task book and the traditional screw oil press design calculation method, after determining the free volume V1 and related dimensions of the screw shaft 26 of the feeding section, the total compression ratio suitable for the low-temperature cold pressing process is selected, and the screw shaft 27 of the pressing section is designed as follows according to the total compression ratio:

[0111] 1) The root circle diameter of the front end of the pressing section spiral shaft 27 is equal to the root circle diameter of the end of the feeding section spiral shaft 26;

[0112] 2) The front end section of the pressing section spiral shaft 27 and the rear end section of the feeding section spiral shaft 26 have the same geometric shape and size;

[0113] 3) Preliminarily determine the pitch S1 of the tooth surface 29, the pitch S2 of the tooth back 30 and the number of turns n of the spiral pressing teeth 25;

[0114] 4) Calculate the axial length of the spiral pressing tooth 25 = S2 × n + 10 (10 represents the width of the sharp corner of the tooth back reserved at the end of the spiral pressing tooth 25);

[0115] 5) Preliminarily determine the root diameter of the tooth back at the end of the spiral pressing tooth 25;

[0116] 6) Calculate the free volume V2 of the last spiral groove 28 of the pressing section;

[0117] 7) Calculate the actual total compression ratio = V1 ÷ V2;

[0118] 8) Compare the calculated total compression ratio with the selected total compression ratio, and adjust the design parameters according to the error until the error between the calculated total compression ratio and the selected total compression ratio meets the requirements.

[0119] In the spiral cold press of the present embodiment, at least one spiral shaft is installed. When a double spiral shaft is used, the two spiral shafts rotate in opposite directions and are installed in combination in the pressing chamber of the spiral cold press.

[0120] The conventional spiral shaft adopts a multi-section combination design, with a large front pitch and a small root diameter, a gradually decreasing rear pitch and an increasing root diameter, and a tapered bushing transition connection between two adjacent spiral assemblies with different root diameters, so that the spiral teeth and the tapered bushing have a large number of sections and a large axial size, with up to 9 sections of the spiral teeth (i.e., spiral teeth) and 6 tapered bushings, which results in the oil being squeezed for a long time and at a high temperature inside the press chamber, which is extremely unfavorable for the low-temperature cold pressing of the oil. The pressing section spiral shaft 27 of this embodiment adopts a tooth surface 2 The double pitch design of the tooth back 9 and the tooth back 30, in conjunction with the frustoconical tooth root circle, makes the spiral groove 28 wide at the front and narrow at the back, deep at the front and shallow at the back. During the movement of the oil from the beginning to the end of the spiral groove 28, the oil is continuously squeezed by the narrowing and shallowing of the spiral groove 28 at every moment, which reduces the number of spiral circles in the pressing chamber, and correspondingly reduces the amount of squeezed oil in the pressing chamber, so that the unit pressure of the squeezed oil in the pressing chamber is greatly improved. This advantage of the present invention can improve the oil output efficiency of the low-temperature cold press and reduce oil loss.

[0121] The operating parameters of the domestically developed SLZ30 twin-screw oil press are as follows:

[0122] 28t peanut kernels are processed daily, roasted and hot pressed, main motor power is 37kw, screw shaft speed is 11rpm, the space volume of the screw shaft in the feeding section is 0.002655m 3 The total number of spiral turns in the press chamber is 16.2, and the bulk density of peanut kernels is 570Kg / m 3 , the peanut kernel content in the pressing chamber is g = 0.002655m 3 ×0.6×2×16.2×570kg / m 3 =29.42kg (0.6 in the formula is the oil filling coefficient of the screw shaft in the feeding section), the axial thrust generated by the screw shaft is 36836Kgf, and the pressure per kilogram of peanut kernels in the pressing chamber is 36836kgf÷29.42kg=1252kgf.

[0123] Among them, the calculation formula for the total number of spiral turns N in the pressing chamber of the SLZ30 double-screw oil press is as follows:

[0124] N=L1÷d1+L2÷d2+(L3+C3)÷d3+(L4+C4)÷d4+(L5+C5)÷d5+(L6+C6)÷d6+(L7+C7)÷d7+(L8+C8)÷d8+L9÷d9

[0125] Among them, Li represents the length of the i-th screw, d i represents the pitch of the i-th screw, i = 1, 2, ..., 9; C j represents the length of the liner corresponding to the j-th pressing screw, j=3, 4, ..., 8; in this embodiment, L1, L2, ..., L9 are 42mm, 170mm, 160mm, 150mm, 140mm, 120mm, 110mm, 90mm, 78mm respectively; the length of No. 1 pressing screw is 42mm, which is its length in the pressing chamber. The total length of No. 1 pressing screw is 364mm, and the remaining length is the lower end of the feed port, which is located outside the pressing chamber and is not involved in the calculation; d1, d2, ..., d9 are 208mm, 114mm, 128mm, 112mm, 96mm, 80mm, 72mm, 64mm, 64mm respectively; C3, C4, ..., C8 are 60mm, 60mm, 70mm, 70mm, 80mm, 90mm respectively; substituting the above parameters into the above formula, N=16.2 turns are calculated.

[0126] Under the conditions of unchanged oil input, unchanged input power, unchanged screw shaft speed, and unchanged total compression ratio, if the pressing section screw shaft 27 of this embodiment is configured in the SLZ30 twin-screw oil press, the total length of the screw shaft can be shortened from the original 1812 mm to 976 mm, and the total number of turns of the spiral pressing teeth 25 in the pressing chamber can be reduced from the original 16.2 turns to 7.59 turns; the effects achieved include:

[0127] Firstly, the oil content in the pressing chamber is reduced from 29.42Kg to 13.78Kg, and the pressure per kilogram of peanut kernels is increased from 1252Kgf to 2712.465Kgf, with the unit pressure increased by 116.65%. If the power of the main motor is reduced to 22kw, the pressure per kilogram of peanut kernels is 1589.4Kgf, which increases the unit pressure of the squeezed oil in the pressing chamber and reduces the output power of the motor, thereby achieving the purpose of energy saving and consumption reduction.

[0128] Secondly, the pressing time of oil in the press chamber is shortened from the original 88.36S to 41.4S, shortened by 53.1%, thereby effectively reducing the pressing temperature in the press chamber.

[0129] In this embodiment, rapeseed is used as the oil material to conduct 4 groups of tests on the operating conditions of the screw oil press. The change of the power consumption of the main motor can be directly reflected by the current of the main motor. The larger the current of the main motor, the greater the operating pressure in the pressing chamber, the higher the temperature, the greater the motor power consumption, and the lower the residual oil rate of the dry cake. In addition, the residual oil rate of the dry cake is also related to the water content of the oil material. The lower the water content of the oil material, the lower the residual oil rate of the dry cake obtained by pressing. Therefore, this embodiment indirectly reflects the improvement effect of the internal operating temperature of the pressing chamber by designing the water-cooling structure of the cage plate and the screw shaft of the screw oil press, and the improvement effect of the residual oil rate of the dry cake by the double pitch design of the tooth surface and tooth back of the screw shaft. The test results are shown in Table 1 below:

[0130] Table 1 Test results of screw oil press operating conditions

[0131] Serial number Oil moisture (%) Main motor current (A) Press chamber operating temperature (℃) Residual oil rate of dry cake (%) 1 10.05±0.4 14 50～55 8.12±0.5 2 5.02±0.4 17 60～65 6.22±0.2 3 6.64±0.2 16 55～60 6.98±0.3 4 6.21±0.5 15 52～60 6.60±0.2

[0132] The dry cake morphology corresponding to the above 4 groups of tests is as follows Fig.12 As shown, Fig.12 (a) Fig.12 (b) Fig.12 (c) Fig.12 (d) Corresponding to the dry cake morphology of the 4 groups tested in Table 1; According to Table 1 and Fig.12 It can be seen that the improved screw oil press according to this embodiment, on the one hand, greatly reduces the operating temperature inside the pressing chamber, and the maximum operating temperature inside the pressing chamber does not exceed 65°C, ensuring that the pressing temperature of the pressing chamber is always maintained within the cold pressing process range below 65°C, thereby greatly improving the quality of the cold-pressed oil; on the other hand, under the condition of ensuring that the pressing temperature of the pressing chamber is below 65°C for cold pressing, the residual oil rate of the dry cake is greatly reduced, and the residual oil rate of the dry cake can be reduced to about 7%, thereby improving the oil output efficiency and reducing oil loss.

[0133] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A new type of cold press with low dry cake residual oil rate, comprising a frame (1), a controller (2), a driving component (3) and a pressing cage (4) mounted on the frame (1), a feeding hopper (5) mounted at the feed end of the pressing cage (4), and a single screw shaft or multiple screw shafts mounted in the pressing cage (4); characterized in that: The pressing cage (4) comprises a plurality of cage plates (6) arranged at intervals along the axial direction, and the opposite side edges of the plurality of cage plates (6) are fixedly connected by a first connecting plate (7) and a second connecting plate (8) respectively; a heat exchange channel is provided on the inner wall of the inner hole of the cage plate (6) along the circumferential direction, and a plurality of pressing bars (11) are arranged adjacent to the side wall of the heat exchange channel along the circumferential direction, and the plurality of pressing bars (11) are surrounded to form a pressing chamber; the heat exchange channel is connected to an external circulation pipeline through a corresponding flow channel; The spiral shaft comprises a feeding section spiral shaft (26) and a pressing section spiral shaft (27), the root circle diameter of the pressing section spiral shaft (27) gradually increases along the axial direction approaching the cake outlet end, the tooth surface (29) pitch S1 and the tooth back (30) pitch S2 of the spiral pressing teeth (25) of the pressing section spiral shaft (27) are two unequal pitches, and the tooth surface (29) pitch S1 is greater than the tooth back (30) pitch S2, and the spiral groove (28) width and depth of the spiral groove (28) of the pressing section spiral shaft (27) both gradually decrease along the axial direction approaching the cake outlet end; A cooling water chamber (31) is provided inside the spiral shaft, and the cooling water chamber (31) is communicated with an external first water inlet pipe (32) and a first water outlet pipe (33).

2. A novel cold press with low dry cake residual oil rate as claimed in claim 1, characterized in that: The heat exchange channel comprises a cooling water trough (9), a sealing sleeve (10) is welded on the opening side of the cooling water trough (9), a plurality of pressing bars (11) are arranged closely along the circumference of the side wall of the sealing sleeve (10), and the cooling water trough (9) is connected to an external circulation pipeline through a corresponding flow channel.

3. A novel cold press with low dry cake residual oil rate as claimed in claim 1, characterized in that: The external circulation pipeline comprises a shunt pipe (12) and a water collecting pipe (13), and the shunt pipe (12) and the water collecting pipe (13) are respectively installed on the first connecting plate (7) and the second connecting plate (8); the shunt pipe (12) is respectively connected to the heat exchange channel of each cage plate (6) through the corresponding first flow channel (14), and the water collecting pipe (13) is respectively connected to the heat exchange channel of each cage plate (6) through the corresponding second flow channel (15); the shunt pipe (12) and the water collecting pipe (13) are respectively connected to the second water inlet pipe (16) and the second water outlet pipe (17).

4. A novel cold press with low dry cake residual oil rate as claimed in claim 3, characterized in that: The cage plate (6) is composed of two semi-annular plates (18), and the two semi-annular plates (18) are detachably connected by a connecting piece; a pressure plate (19) is fixedly installed at both ends of the inner hole of each semi-annular plate (18), and a plurality of pressing bars (11) are arranged closely between the two pressure plates (19); the heat exchange channel and the sealing sleeve (10) are both two-section split structures, and the openings at both ends of the heat exchange channel are provided with sealing plugs (20); the first connecting plate (7), the second connecting plate (8), the diverter pipe (12), the water collecting pipe (13), the first flow channel (14), and the second flow channel (15) are each provided with two groups, which are respectively used for circulating water in the heat exchange channels inside the two semi-annular plates (18).

5. A novel cold press with low dry cake residual oil rate as claimed in claim 4, characterized in that: The connecting member comprises a bolt (21), a pin (22) and an ear plate (23); the sides of the two first connecting plates (7) and the second connecting plates (8) are provided with through holes for installing the bolts (21); the through holes are provided between two adjacent cage plates (6); the two first connecting plates (7) and the two second connecting plates (8) are connected by bolts (21) respectively; the bottom ends of the two second connecting plates (8) are provided with ear plates (23); the pin (22) passes through the shaft holes (36) of the four ear plates (23) in sequence.

6. A novel cold press with low dry cake residual oil rate as claimed in claim 1, characterized in that: The length L of the screw shaft (27) of the pressing section is S2×n+b2, wherein n represents the number of turns of the screw teeth (25), and b2 represents the axial width of the end of the screw teeth (25).

7. A novel cold press with low dry cake residual oil rate as claimed in claim 1, characterized in that: The end width l of the spiral groove (28) is S2×n-b1-S1×(n-1), wherein n represents the number of turns of the spiral pressing tooth (25), and b1 represents the axial width of the starting end of the spiral pressing tooth (25).

8. A novel cold press with low dry cake residual oil rate as claimed in claim 1, characterized in that: The two ends of the spiral shaft are respectively connected to a power input shaft (34) and a rotating support shaft (35), and the spiral pressing teeth (25) are integrally formed with the spiral shaft; the rotating support shaft (35) is a hollow shaft, and the shaft hole (36) of the rotating support shaft (35) is connected to the cooling water chamber (31), and the first water inlet pipe (32) and the first water outlet pipe (33) are installed at the ends of the rotating support shaft (35); a bearing assembly is installed on the outside of the rotating support shaft (35), and a cover (37) is sealed on the outer end surface of the bearing assembly; one end of the first water inlet pipe (32) is located outside the cover (37), and the other end is located inside the cover (37) and extends to the inside of the cooling water chamber (31), and the first water outlet pipe (33) is installed on the outside of the bottom of the cover (37).

9. A novel cold press with low dry cake residual oil rate as claimed in claim 8, characterized in that: The bearing assembly comprises a bearing sleeve (38) fixedly sleeved on the outside of a rotating support shaft (35); a roller bearing (39) is sleeved on the outside of the bearing sleeve (38); a bearing seat (40) is sleeved on the outside of the roller bearing (39); a bearing cover (41) is provided at the front and rear ends of the bearing seat (40); an open end of the cover shell (37) is sealed and welded to the bearing cover (41) at the front end of the bearing seat (40); and an oil seal element (42) is provided between the inner side of the bearing cover (41) and the bearing sleeve (38).

10. A method for cooling a pressing chamber, based on the novel cold press according to any one of claims 1 to 9, characterized in that: The following steps are involved: Real-time monitoring of operating temperature data in the pressing chamber; According to the monitored temperature data, the external circulation pipeline is controlled to circulate the cooling medium into the heat exchange channel of the cage plate (6), and the first water inlet pipe (32) and the first water outlet pipe (33) are controlled to circulate the cooling medium into the cooling water cavity (31) inside the spiral shaft; The higher the operating temperature in the press chamber, the greater the flow rate and faster the flow rate of the cooling medium circulation.

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