CA2224208A1 - Hydraulic pressure boosting unit, in particular for a press operating in accordance with the high inner pressure shaping process - Google Patents
Hydraulic pressure boosting unit, in particular for a press operating in accordance with the high inner pressure shaping process Download PDFInfo
- Publication number
- CA2224208A1 CA2224208A1 CA002224208A CA2224208A CA2224208A1 CA 2224208 A1 CA2224208 A1 CA 2224208A1 CA 002224208 A CA002224208 A CA 002224208A CA 2224208 A CA2224208 A CA 2224208A CA 2224208 A1 CA2224208 A1 CA 2224208A1
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- Canada
- Prior art keywords
- docking
- piston rod
- piston
- hydraulic pressure
- boosting unit
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D26/00—Shaping without cutting otherwise than using rigid devices or tools or yieldable or resilient pads, i.e. applying fluid pressure or magnetic forces
- B21D26/02—Shaping without cutting otherwise than using rigid devices or tools or yieldable or resilient pads, i.e. applying fluid pressure or magnetic forces by applying fluid pressure
- B21D26/033—Deforming tubular bodies
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
- Actuator (AREA)
- Press Drives And Press Lines (AREA)
- Electric Double-Layer Capacitors Or The Like (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A hydraulic pressure boosting unit (11) is used in particular in a press operating according to the high inner pressure extrusion process. The hydraulic pressure boosting unit has a docking cylinder (10) with a docking piston that slides in a first cylinder chamber (15) and a docking piston rod (26) secured to the docking piston projects outwards through a housing head (20). The hydraulic pressure boosting unit has a pressure booster (11) with a primary piston (40) located in a second cylinder chamber (16) coaxial to the first cylinder chamber and separated from the first cylinder chamber by a housing bottom (17) and with a secondary piston (41) that plunges into a central axial bore (28) of the docking piston and docking piston rod. In order to generate high forces with the docking cylinder, only one side of the docking piston has a piston rod, namely the docking piston rod.
Description
CA 02224208 1997-12-08 ~ Gp~
SPECIFICATION
HYDRAULIC PRESSURE BOOSTING UNIT, IN PARTICULAR, FOR A PRESS OPERATING IN ACCORDANCE WITH THE
HIGH INNER PRESSURE SHAPING PROCESS
The present invention proceeds from a hydraulic pressure boosting unit which is used, in particular, in a press operating in accordance with the high inner pressure shaping process which has the features set forth in the preamble to Claim 1.
Such a hydraulic pressure boosting unit is known, for instance, from Federal Republic of Germany Utility Model 18 85 909 or from Federal Republic of Germany 43 12 589 A1. In those pressure boosting units, the docking cylinder has a docking piston to which a docking piston rod is attached, the rod, seen from the primary piston of the pressure boosting unit, passing outward through a housing head which is present on the other side of the docking piston. Docking piston and docking piston rod are provided with a central bore hole into which the secondary piston of the pressure booster extends.
The docking piston also bears, on the side thereof facing the primary piston of the pressure booster a piston rod which also has the central bore hole in longitudinal direction. In the pressure boosting unit of the utility model, this second piston rod of the docking piston extends towards the outside through a housing bottom. In the pressure boosting unit of DE 43 12 589 A1, in which the housing bottom directly separates the first cylinder chamber from the second cylinder chamber, the second piston rod of the docking cylinder extends merely into the bottom of the housing.
In hydraulic pressure boosting units of the type in question, the object of the docking cylinder is, first of all, to hold a blank closed, the blank generally consisting of a length of tube. Furthermore, in many forming processes it has the function of pushing material axially forward upon the forming.
The object of the invention is so further to develop a hydraulic pressure boosting unit having the features set forth in the preamble to Claim 1 that greater forces than previously can be exerted by the docking cylinder and that a shorter structural length is possible.
This object is achieved in accordance with the invention in the manner that, a hydraulic pressure boosting unit having the features set forth in the preamble to Claim 1 is characterized by the fact that only one side of the docking piston has a piston rod, namely the docking piston rod which extends outward through the housing head. In this way, the inside diameter of the annular surface present on the side of the docking piston lying opposite the docking piston rod is reduced to the outside diameter of the secondary piston of the pressure booster. The annular surface is thus increased as compared with the known hydraulic pressure boosting units, so that a greater force can be exerted without increasing the outside diameter of the docking piston and without increasing the pressure which acts. Furthermore, the unit is now of shorter length, since the first cylinder chamber and the second cylinder chamber can be brought closer together.
The dependent claims contain advantageous developments of a hydraulic pressure boosting unit in accordance with the invention, which refer to the sealing of different pressure chambers from each other and the leading away of leakage liquid.
One embodiment of a hydraulic pressure boosting unit in accordance with the invention is shown diagrammatically in the drawing, in its entirety and in views of the structural details. The invention will now be explained in further detail with reference to these drawings.
In the drawings Fig. 1 diagrammatically shows the entire embodiment;
Fig. 2 shows, in detail, a portion within the region of two leakage-liquid channels passing through the docking piston rod; and Fig. 3 is a section along the line III-III of Fig. 2.
The hydraulic pressure boosting unit shown in the drawing comprises a docking cylinder 10, a pressure booster 11, and a fast-motion cylinder 12 for the pressure booster 11. The parts which have been mentioned with respect to their function cannot be unequivocally separated in space from each other but are integrated in one another, forming a compact unit. The housing 13 of the unit comprises a single piece housing central part 14 which is common to the docking cylinder 10 and the pressure booster 11 and has a first cylinder chamber 15 and a second cylinder chamber 16. The two cylinder chambers 15 and 16 are open on opposite sides and are separated from each other by a bottom 17 of the housing central part 14 from which the cylinder walls 18 and 19 of the two cylinder chambers extend in opposite directions. The first cylinder chamber 15 is closed by a housing head 20 and the second cylinder chamber 16 is closed by a housing head 21.
The first cylinder chamber 15 belongs to the docking cylinder 10. In it, there is axially displaceable a docking piston 25 which has a piston rod secured to it only on one side. This rod extends outward as docking piston rod 26 through the housing head 20. On its free end, there is screwed a flange 27 by which a tubular blank 37 which is to be shaped is closed. A central bore hole 28 extends axially through the docking piston 25 and through the docking piston rod 26, this hole having a section 29 of smaller diameter and a section 30 of larger diameter. The latter section extends from the end of the docking piston rod 26 facing the flange 27 up to a radial shoulder 31, which, even when the docking piston rod 26 is fully retracted, is still spaced axially from the housing head 20.
Docking piston rod 26 and housing head 20 are sealed-off from each other by means of two axially spaced packings 32 and 33, from between which a leakage line 34 extends outward.
A hydraulic oil can flow through two connections 35 and 36 through the cylinder wall 18 in and out of the two partial chambers 15a and 15b of the cylinder chamber 15, which are separated from each other by the docking piston 25.
The primary piston 40 of the pressure booster 11 is displaceable in the second cylinder chamber 16, it dividing the cylinder chamber 16 into the two partial chambers 16a and 16b. The secondary piston 41 of the pressure booster 11, which piston if of a substantially smaller diameter than the primary piston 40, extends like a piston rod on one side from the primary piston 40, passes through the bottom 17 of the housing central part 14, and enters into the central bore hole 28 of the docking piston 25 and of the docking piston rod 26 until extending into the section 30 of the hole. The step 31 in the bore hole 28 is not moved over by the free end of the docking piston rod 26 in any phase of an operating cycle of the pressure boosting unit. The free end of the secondary piston 41 is therefore always axially outside of the housing head 20.
On the primary piston 40 of the pressure booster 11 there is fastened, in addition to the secondary piston 41, a piston rod 42 which protrudes in direction opposite the secondary piston 41, which rod passes through a bore hole 43 in the housing head 21 into a cylinder chamber 44 developed in said housing head and bears there a fast-motion piston 45.
The cylinder chamber 44 is closed by a cover 46. The fast-motion piston 45 divides the cylinder chamber 44 into two partial chambers 44a and 44b, which can be supplied with a pressurized fluid via channels 47 and 48 in the housing head 41. For this there is provided a pressurized fluid having a base of water. Through the piston rod 42, the primary piston 40 and the secondary piston 41 of the pressure booster 11, there extends centrally a channel 49 which is connected by a transverse hole 50 with the one partial chamber 44a of the cylinder chamber 44 which is supplied with pressurized fluid via the channel 48 and at the mouth of which channel into the section 30 of the hole 48, a non-return valve 51 is present, blocking off from the channel 48.
The primary piston 40 of the pressure booster 11 can be acted on by pressure alternately on its two sides through the channels 52 and 53 which pass through the cylinder wall 19.
A number of packings are provided in order to separate the different pressure chambers and the different hydraulic fluids from each other. Three packings 60, 61, and 62 which are spaced axially from each other are arranged in the bore hole 43 between the housing head 21 and the piston rod 42.
From between the packings 60 and 61 there extends a leakage line 63, in which hydraulic fluid having a water base which leaks out of the partial chamber 44a of the cylinder chamber 44 over the packing 60 is discharged. Between the packings 61 and 62 there extends outward a leakage line 64 via which hydraulic oil which leaks out of the partial chamber 16a of the cylinder chamber 16 over the packing 62 is discharged.
In the bottom 17 of the housing central part 14, between the secondary piston 41 of the pressure booster and the bottom, at an axial distance from each other, there are two packings 65 and 66 from between which a leakage line 67 extends, which line, as is customary for a leakage line, is connected to the tank and which prevents the pressures in the two partial chambers 15a and 16b of the cylinder chambers 15 and 16 which are separated from each other by the bottom 17 from influencing each other.
Between the partial chamber 15a of the cylinder chamber 15 which can be acted on by hydraulic oil via the channel 35 and the section 30 of the bore hole 28 which can be acted on by hydraulic fluid having a base of water, there are again three packings which are arranged, fixed in position relative to the docking piston and the docking piston rod, in the section 29 of the bore hole 28 between the docking piston 25 and the docking piston rod 26, on the one hand, and the secondary piston 41, on the other hand. The packing 68 is directly behind the piston-side start of the bore hole 28 in the docking piston 25. The two other packings 69 and 70 are located just in front of the step 31 in radial planes which, even when the docking piston rod is completely retracted, protrude in front of the housing head 20. As can be noted from Fig. 2, the packing 63, corresponding to the two possible directions of movement between the docking piston rod 26 and the secondary piston 41, consist of two packing rings 80 and 81 which are axially spaced from each other.
The other packings which can be noted in Fig. 1 can also be formed in each case of several packing rings.
Between the two packings 69 and 70 there is a leakage line 71 for the hydraulic fluid which leaks out from the section 30 of the bore hole 28 over the packing 70, the line passing transversely through the docking piston rod 26 towards the outside. Another leakage line 72 is also present in each position of the docking piston rod 26 in front of the housing head 20, and passes transversely through the docking piston rod 26, discharging between the two packings 68 and 69 into the section 29 of the bore hole 28. Via it, hydraulic oil which leaks out over the packing 68 is discharged.
Both leakage lines 71 and 72 are formed by a bore hole which extends from a flattening 82 on the docking piston rod 26. The mouth openings of the two bore holes in the flat 82 are located in the same radial plane 83 of the docking piston rod 26 and are at a distance from each other which is less than the diameter of the section 29 of the central bore hole 28 in the docking piston rod 26. From the mouth openings, the bore holes 71 and 72 extend axially in opposite directions, but parallel to each other towards the inside in a projected view on the radial plane 83, and discharge on opposite sides of the packing 69 into the bore hole 28.
Since a tube or tubing hose can be fastened only with difficulty directly to the flat 82 because of the narrow space between the housing head 20 and a flange 84 of the docking piston rod, which is not shown in Fig. 1, a narrow plate 85 is screwed onto the flat 82 by long screws 86, in which plate the bore holes 71 and 72 are continued by bore holes 87 and 88 up to about the outer periphery of the flange 84 and of the housing 13. There, two tubes can easily be fastened to the plate 85.
If one proceeds from a condition such as shown in Fig.
l, then, in operation, the docking piston 25 first of all pushes the flange 27 close to the blank 37 which is to be shaped. Via the channel 48, the partial chamber 44a of the cylinder chamber 44, the transverse bore hole 50, the longitudinal bore hole 49, the non-return valve 51, the section 30 of the bore hole 28, and a bore hole 75 in the flange 27, hydraulic fluid having a base of water is forced into the blank, whereby the air escapes from the blank through a slot between flange and blank, together with hydraulic fluid. The pressure in the blank increases. At a given pressure, the blank is considered full and is closed by the docking cylinder. The partial chamber 44a is relieved of pressure. The non-return valve 51 closes. The fast-motion piston 45 is now acted on by pressure via the channel 47 and the partial chamber 44b and pushes the secondary piston 41 of the pressure booster 11 deeper into the bore hole 28. Since a maximum pressure cannot be exceeded in the channel 47, displacement of the secondary piston 41 with the help of the fast-motion piston 45 is possible only up to a given pressure in the blank to be shaped. As from this pressure, the primary piston 40 of the pressure booster 11 is acted on by pressure via the channel 52 in addition to the fast-motion piston 45.
During the shaping of the blank 37, the docking piston 25 can be moved further in order to axially push up material of the blank.
After the completion of the shaping process, the fluid in the shaped part is decompressed, first of all by a partial withdrawal of the primary piston 40 and of the secondary piston 41 of the pressure booster 11. Thereupon the pistons 40 and 41 of the pressure booster 11 and of the docking piston 25 are again brought into the initial position shown in the drawing.
SPECIFICATION
HYDRAULIC PRESSURE BOOSTING UNIT, IN PARTICULAR, FOR A PRESS OPERATING IN ACCORDANCE WITH THE
HIGH INNER PRESSURE SHAPING PROCESS
The present invention proceeds from a hydraulic pressure boosting unit which is used, in particular, in a press operating in accordance with the high inner pressure shaping process which has the features set forth in the preamble to Claim 1.
Such a hydraulic pressure boosting unit is known, for instance, from Federal Republic of Germany Utility Model 18 85 909 or from Federal Republic of Germany 43 12 589 A1. In those pressure boosting units, the docking cylinder has a docking piston to which a docking piston rod is attached, the rod, seen from the primary piston of the pressure boosting unit, passing outward through a housing head which is present on the other side of the docking piston. Docking piston and docking piston rod are provided with a central bore hole into which the secondary piston of the pressure booster extends.
The docking piston also bears, on the side thereof facing the primary piston of the pressure booster a piston rod which also has the central bore hole in longitudinal direction. In the pressure boosting unit of the utility model, this second piston rod of the docking piston extends towards the outside through a housing bottom. In the pressure boosting unit of DE 43 12 589 A1, in which the housing bottom directly separates the first cylinder chamber from the second cylinder chamber, the second piston rod of the docking cylinder extends merely into the bottom of the housing.
In hydraulic pressure boosting units of the type in question, the object of the docking cylinder is, first of all, to hold a blank closed, the blank generally consisting of a length of tube. Furthermore, in many forming processes it has the function of pushing material axially forward upon the forming.
The object of the invention is so further to develop a hydraulic pressure boosting unit having the features set forth in the preamble to Claim 1 that greater forces than previously can be exerted by the docking cylinder and that a shorter structural length is possible.
This object is achieved in accordance with the invention in the manner that, a hydraulic pressure boosting unit having the features set forth in the preamble to Claim 1 is characterized by the fact that only one side of the docking piston has a piston rod, namely the docking piston rod which extends outward through the housing head. In this way, the inside diameter of the annular surface present on the side of the docking piston lying opposite the docking piston rod is reduced to the outside diameter of the secondary piston of the pressure booster. The annular surface is thus increased as compared with the known hydraulic pressure boosting units, so that a greater force can be exerted without increasing the outside diameter of the docking piston and without increasing the pressure which acts. Furthermore, the unit is now of shorter length, since the first cylinder chamber and the second cylinder chamber can be brought closer together.
The dependent claims contain advantageous developments of a hydraulic pressure boosting unit in accordance with the invention, which refer to the sealing of different pressure chambers from each other and the leading away of leakage liquid.
One embodiment of a hydraulic pressure boosting unit in accordance with the invention is shown diagrammatically in the drawing, in its entirety and in views of the structural details. The invention will now be explained in further detail with reference to these drawings.
In the drawings Fig. 1 diagrammatically shows the entire embodiment;
Fig. 2 shows, in detail, a portion within the region of two leakage-liquid channels passing through the docking piston rod; and Fig. 3 is a section along the line III-III of Fig. 2.
The hydraulic pressure boosting unit shown in the drawing comprises a docking cylinder 10, a pressure booster 11, and a fast-motion cylinder 12 for the pressure booster 11. The parts which have been mentioned with respect to their function cannot be unequivocally separated in space from each other but are integrated in one another, forming a compact unit. The housing 13 of the unit comprises a single piece housing central part 14 which is common to the docking cylinder 10 and the pressure booster 11 and has a first cylinder chamber 15 and a second cylinder chamber 16. The two cylinder chambers 15 and 16 are open on opposite sides and are separated from each other by a bottom 17 of the housing central part 14 from which the cylinder walls 18 and 19 of the two cylinder chambers extend in opposite directions. The first cylinder chamber 15 is closed by a housing head 20 and the second cylinder chamber 16 is closed by a housing head 21.
The first cylinder chamber 15 belongs to the docking cylinder 10. In it, there is axially displaceable a docking piston 25 which has a piston rod secured to it only on one side. This rod extends outward as docking piston rod 26 through the housing head 20. On its free end, there is screwed a flange 27 by which a tubular blank 37 which is to be shaped is closed. A central bore hole 28 extends axially through the docking piston 25 and through the docking piston rod 26, this hole having a section 29 of smaller diameter and a section 30 of larger diameter. The latter section extends from the end of the docking piston rod 26 facing the flange 27 up to a radial shoulder 31, which, even when the docking piston rod 26 is fully retracted, is still spaced axially from the housing head 20.
Docking piston rod 26 and housing head 20 are sealed-off from each other by means of two axially spaced packings 32 and 33, from between which a leakage line 34 extends outward.
A hydraulic oil can flow through two connections 35 and 36 through the cylinder wall 18 in and out of the two partial chambers 15a and 15b of the cylinder chamber 15, which are separated from each other by the docking piston 25.
The primary piston 40 of the pressure booster 11 is displaceable in the second cylinder chamber 16, it dividing the cylinder chamber 16 into the two partial chambers 16a and 16b. The secondary piston 41 of the pressure booster 11, which piston if of a substantially smaller diameter than the primary piston 40, extends like a piston rod on one side from the primary piston 40, passes through the bottom 17 of the housing central part 14, and enters into the central bore hole 28 of the docking piston 25 and of the docking piston rod 26 until extending into the section 30 of the hole. The step 31 in the bore hole 28 is not moved over by the free end of the docking piston rod 26 in any phase of an operating cycle of the pressure boosting unit. The free end of the secondary piston 41 is therefore always axially outside of the housing head 20.
On the primary piston 40 of the pressure booster 11 there is fastened, in addition to the secondary piston 41, a piston rod 42 which protrudes in direction opposite the secondary piston 41, which rod passes through a bore hole 43 in the housing head 21 into a cylinder chamber 44 developed in said housing head and bears there a fast-motion piston 45.
The cylinder chamber 44 is closed by a cover 46. The fast-motion piston 45 divides the cylinder chamber 44 into two partial chambers 44a and 44b, which can be supplied with a pressurized fluid via channels 47 and 48 in the housing head 41. For this there is provided a pressurized fluid having a base of water. Through the piston rod 42, the primary piston 40 and the secondary piston 41 of the pressure booster 11, there extends centrally a channel 49 which is connected by a transverse hole 50 with the one partial chamber 44a of the cylinder chamber 44 which is supplied with pressurized fluid via the channel 48 and at the mouth of which channel into the section 30 of the hole 48, a non-return valve 51 is present, blocking off from the channel 48.
The primary piston 40 of the pressure booster 11 can be acted on by pressure alternately on its two sides through the channels 52 and 53 which pass through the cylinder wall 19.
A number of packings are provided in order to separate the different pressure chambers and the different hydraulic fluids from each other. Three packings 60, 61, and 62 which are spaced axially from each other are arranged in the bore hole 43 between the housing head 21 and the piston rod 42.
From between the packings 60 and 61 there extends a leakage line 63, in which hydraulic fluid having a water base which leaks out of the partial chamber 44a of the cylinder chamber 44 over the packing 60 is discharged. Between the packings 61 and 62 there extends outward a leakage line 64 via which hydraulic oil which leaks out of the partial chamber 16a of the cylinder chamber 16 over the packing 62 is discharged.
In the bottom 17 of the housing central part 14, between the secondary piston 41 of the pressure booster and the bottom, at an axial distance from each other, there are two packings 65 and 66 from between which a leakage line 67 extends, which line, as is customary for a leakage line, is connected to the tank and which prevents the pressures in the two partial chambers 15a and 16b of the cylinder chambers 15 and 16 which are separated from each other by the bottom 17 from influencing each other.
Between the partial chamber 15a of the cylinder chamber 15 which can be acted on by hydraulic oil via the channel 35 and the section 30 of the bore hole 28 which can be acted on by hydraulic fluid having a base of water, there are again three packings which are arranged, fixed in position relative to the docking piston and the docking piston rod, in the section 29 of the bore hole 28 between the docking piston 25 and the docking piston rod 26, on the one hand, and the secondary piston 41, on the other hand. The packing 68 is directly behind the piston-side start of the bore hole 28 in the docking piston 25. The two other packings 69 and 70 are located just in front of the step 31 in radial planes which, even when the docking piston rod is completely retracted, protrude in front of the housing head 20. As can be noted from Fig. 2, the packing 63, corresponding to the two possible directions of movement between the docking piston rod 26 and the secondary piston 41, consist of two packing rings 80 and 81 which are axially spaced from each other.
The other packings which can be noted in Fig. 1 can also be formed in each case of several packing rings.
Between the two packings 69 and 70 there is a leakage line 71 for the hydraulic fluid which leaks out from the section 30 of the bore hole 28 over the packing 70, the line passing transversely through the docking piston rod 26 towards the outside. Another leakage line 72 is also present in each position of the docking piston rod 26 in front of the housing head 20, and passes transversely through the docking piston rod 26, discharging between the two packings 68 and 69 into the section 29 of the bore hole 28. Via it, hydraulic oil which leaks out over the packing 68 is discharged.
Both leakage lines 71 and 72 are formed by a bore hole which extends from a flattening 82 on the docking piston rod 26. The mouth openings of the two bore holes in the flat 82 are located in the same radial plane 83 of the docking piston rod 26 and are at a distance from each other which is less than the diameter of the section 29 of the central bore hole 28 in the docking piston rod 26. From the mouth openings, the bore holes 71 and 72 extend axially in opposite directions, but parallel to each other towards the inside in a projected view on the radial plane 83, and discharge on opposite sides of the packing 69 into the bore hole 28.
Since a tube or tubing hose can be fastened only with difficulty directly to the flat 82 because of the narrow space between the housing head 20 and a flange 84 of the docking piston rod, which is not shown in Fig. 1, a narrow plate 85 is screwed onto the flat 82 by long screws 86, in which plate the bore holes 71 and 72 are continued by bore holes 87 and 88 up to about the outer periphery of the flange 84 and of the housing 13. There, two tubes can easily be fastened to the plate 85.
If one proceeds from a condition such as shown in Fig.
l, then, in operation, the docking piston 25 first of all pushes the flange 27 close to the blank 37 which is to be shaped. Via the channel 48, the partial chamber 44a of the cylinder chamber 44, the transverse bore hole 50, the longitudinal bore hole 49, the non-return valve 51, the section 30 of the bore hole 28, and a bore hole 75 in the flange 27, hydraulic fluid having a base of water is forced into the blank, whereby the air escapes from the blank through a slot between flange and blank, together with hydraulic fluid. The pressure in the blank increases. At a given pressure, the blank is considered full and is closed by the docking cylinder. The partial chamber 44a is relieved of pressure. The non-return valve 51 closes. The fast-motion piston 45 is now acted on by pressure via the channel 47 and the partial chamber 44b and pushes the secondary piston 41 of the pressure booster 11 deeper into the bore hole 28. Since a maximum pressure cannot be exceeded in the channel 47, displacement of the secondary piston 41 with the help of the fast-motion piston 45 is possible only up to a given pressure in the blank to be shaped. As from this pressure, the primary piston 40 of the pressure booster 11 is acted on by pressure via the channel 52 in addition to the fast-motion piston 45.
During the shaping of the blank 37, the docking piston 25 can be moved further in order to axially push up material of the blank.
After the completion of the shaping process, the fluid in the shaped part is decompressed, first of all by a partial withdrawal of the primary piston 40 and of the secondary piston 41 of the pressure booster 11. Thereupon the pistons 40 and 41 of the pressure booster 11 and of the docking piston 25 are again brought into the initial position shown in the drawing.
Claims (10)
1. A hydraulic pressure boosting unit, in particular for a press operating in accordance with the high inner pressure shaping process, having a docking cylinder (10) which has a docking piston (25) which is displaceable within a first cylinder chamber (15) and a docking piston rod (26) which is fastened to the docking piston (25) and extends towards the outside through a housing head (20), and is provided with a pressure booster (11) the primary piston (40) of which is arranged in a second cylinder chamber (16) arranged coaxial to the first cylinder chamber and separated from the first cylinder chamber (15) by a housing bottom (17), and the secondary piston (41) of which extends into a central bore hole (28) of the docking piston (25) and of the docking piston rod (26), characterized by the fact that the docking piston (25) has a piston rod (26) only on one side.
2. A hydraulic pressure boosting unit according to Claim 1, characterized by the fact that, between the docking piston (25) and/or the docking-piston rod (26) on the one hand and the secondary piston (41) of the pressure booster (11) on the other hand, there are two packings (69, 70; 68, 69) spaced axially apart from each other, and that between the two packings of the slot between the secondary piston (41) and the docking piston (25) and/or the docking piston rod (26) a leakage liquid channel (71, 72) leading to the outside extends.
3. A hydraulic pressure boosting unit according to Claim 2, characterized by the fact that the leakage liquid channel (71, 72) leads directly to the outside through the docking-piston rod (26) and terminates preferably radially on the outside of the docking piston rod (26).
4. A hydraulic pressure boosting unit according to Claim 3, characterized by the fact that the secondary piston (41) extends in every position and in every position of the docking piston rod (26) up to beyond the housing head (20) into the docking piston rod (26); that one of the packings (69; 70) is located outside the housing head (20); and that the leakage liquid channel (71, 72) is formed by a bore hole which extends at least approximately transversely through the docking piston rod (26) and discharges towards the outside in front of the housing head (20).
5. A hydraulic pressure boosting unit according to any of Claims 2 to 4, characterized by the fact that between the docking piston (25) and/or the docking piston rod (26) on the one hand and the secondary piston (41) on the other hand, three packings (68, 69, 70) spaced axially apart from each other are arranged, and that an outwardly extending leakage liquid channel (71, 72) extends in each case axially on both sides of the central packing (69).
6. A hydraulic pressure boosting unit according to Claim 5, characterized by the fact that the two leakage liquid channels (71, 72) terminate on the outside of the docking piston rod (26) in the same radial plane of the docking piston rod (26) and staggered laterally with respect to each other.
7. A hydraulic pressure boosting unit according to Claim 6, characterized by the fact that the two leakage liquid channels (71, 72) terminate on the outside of the docking piston rod (26) in a flat (82).
8. A hydraulic pressure boosting unit according to Claim 6 or 7, characterized by the fact that the lateral stagger of the leakage liquid channels (71, 72) is less than the diameter of the central bore hole (28) in the docking piston rod (26), and that the two leakage liquid channels (71, 72) extend obliquely only along the docking piston rod (26).
9. A hydraulic pressure boosting unit according to any of Claims 3 to 8, characterized by the fact that a plate (89) having a bore hole or several bore holes (87, 88) which continue the leakage liquid channel or channels (71, 72) is fastened radially on the outside of the docking piston rod (26).
10. A hydraulic pressure boosting unit according to any of Claims 2 to 9, characterized by the fact that the packings (68, 69, 70) acting between docking piston (25) and/or docking piston rod (26) on the one hand and the secondary piston (41) on the other hand are arranged at rest with respect to the docking piston (25) and the docking piston rod (26) respectively.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19521101.4 | 1995-06-09 | ||
| DE19521101A DE19521101A1 (en) | 1995-06-09 | 1995-06-09 | Hydraulic pressure intensifier unit, in particular for a press working according to the hydroforming process |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2224208A1 true CA2224208A1 (en) | 1996-12-27 |
Family
ID=7764032
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002224208A Abandoned CA2224208A1 (en) | 1995-06-09 | 1996-06-07 | Hydraulic pressure boosting unit, in particular for a press operating in accordance with the high inner pressure shaping process |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP0830221B1 (en) |
| JP (1) | JPH11509479A (en) |
| AT (1) | ATE176414T1 (en) |
| CA (1) | CA2224208A1 (en) |
| CZ (1) | CZ396097A3 (en) |
| DE (2) | DE19521101A1 (en) |
| WO (1) | WO1996041692A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE9904464D0 (en) * | 1999-12-07 | 1999-12-07 | Jan Ericson Med Firma J Tec | Apparatus for generating hydraulic pressure |
| EP2298940B1 (en) * | 2009-08-25 | 2012-08-08 | Felss Burger GmbH | Automatic frettage (interference fit) device for high pressure components, particularly for pipelines |
| FR2965247B1 (en) * | 2010-09-27 | 2012-09-28 | Snecma | HYDRAULIC DEVICE FOR CHANGING NO PROPELLATION |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1185437A (en) * | 1968-09-09 | 1970-03-25 | Masanobu Nakamura | Bulging Apparatus. |
| CS188679B1 (en) * | 1977-04-05 | 1979-03-30 | Jindrich Spacek | Facility for the hydromechanic drawing |
| BG39831A1 (en) * | 1983-01-26 | 1986-09-15 | Petkov | Method and device for processing of blanks by hydroplastic forming |
| US4580427A (en) * | 1984-12-13 | 1986-04-08 | Eisho Seisakusho Co., Ltd. | Method for manufacturing ornamented head lug pipes |
| DE4133188A1 (en) * | 1990-10-08 | 1992-04-09 | Zahnradfabrik Friedrichshafen | Sealing unit for pressurised chambers, - is esp. used with pistons and piston rods and consists of sealing rings with leakage chamber between and leakage pipe |
| DE4312589C2 (en) * | 1992-10-27 | 1998-07-09 | Mannesmann Rexroth Ag | Hydraulic system for a forming press |
-
1995
- 1995-06-09 DE DE19521101A patent/DE19521101A1/en not_active Withdrawn
-
1996
- 1996-06-07 JP JP9502605A patent/JPH11509479A/en active Pending
- 1996-06-07 WO PCT/EP1996/002489 patent/WO1996041692A1/en not_active Application Discontinuation
- 1996-06-07 CA CA002224208A patent/CA2224208A1/en not_active Abandoned
- 1996-06-07 AT AT96921949T patent/ATE176414T1/en not_active IP Right Cessation
- 1996-06-07 CZ CZ973960A patent/CZ396097A3/en unknown
- 1996-06-07 DE DE59601271T patent/DE59601271D1/en not_active Expired - Fee Related
- 1996-06-07 EP EP96921949A patent/EP0830221B1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| DE59601271D1 (en) | 1999-03-18 |
| CZ396097A3 (en) | 1999-05-12 |
| JPH11509479A (en) | 1999-08-24 |
| ATE176414T1 (en) | 1999-02-15 |
| DE19521101A1 (en) | 1996-12-12 |
| EP0830221B1 (en) | 1999-02-03 |
| EP0830221A1 (en) | 1998-03-25 |
| WO1996041692A1 (en) | 1996-12-27 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |