EP2551529B1 - Multiplicateur de pression - Google Patents

Description

The invention relates to a portable pressure booster for driving interchangeable hydraulic tools, with a gas or air pressure driven pneumatic unit, connected to the pneumatic unit hydraulic unit and a coupling unit for immovable and detachable connection of the hydraulic tool to the hydraulic unit, wherein the pneumatic unit, the hydraulic unit and the coupling unit to a one-piece mobile handling unit are summarized.

Portable pressure intensifiers can be used in industrial manufacturing for the hydraulic drive of a variety of tools, such as riveting, punching, drilling or cutting tools. To operate such pressure booster an additional power connection is required in addition to a gas or air pressure connection. The disadvantage of this is that for the operation of the pressure booster an additional voltage conversion adapted to the voltage used in this country must be made. In particular, this makes international distribution more difficult.

A pressure booster of the type mentioned with a connected to the pneumatic unit hydraulic unit is for example from the EP 0 143 730 A1 , of the JP 11114855 A and the JP 11245177 A known. A coupling unit for liquid-tight connection of two components is in the US 3,413,018 A described. Pressure intensifiers with interchangeable tools have the problem that the connection between pressure intensifier and hydraulic tool is often not sufficiently stable to work with high forces. For this reason, pressure intensifiers designed for high forces are not designed for the interchangeable connection of hydraulic tools or massively shaped such that the pressure intensifiers can only be operated with auxiliary devices due to their size and / or their weight.

In the case of replaceable hydraulic tools, it is aggravating that replacement of the hydraulic tool is usually accompanied by losses of hydraulic fluid in the area of the coupling. In particular by dripping hydraulic fluid, eg. In industrial area, there is a particularly high risk of occupational accidents, only by additional work, such as the wiping down the dropped hydraulic fluid can be avoided. However, such disruptions are not acceptable in today's industrial manufacturing.

It is therefore an object of the invention to provide an easily manageable, particularly compact, suitable for high workload pressure booster, which allows a more secure and fast replacement of tools.

This object is achieved by a portable pressure booster according to claim 1. Advantageous developments of the invention are specified in the dependent claims.

The inventive portable pressure booster for driving replaceable hydraulic tools has a gas or pneumatic driven pneumatic unit, a connected to the pneumatic unit hydraulic unit and a coupling unit for immovable and detachable connection of the hydraulic tool to the hydraulic unit, wherein the pneumatic unit, the hydraulic unit and the coupling unit to a one-piece, mobile handling unit are summarized.

The inventive pressure intensifier is particularly advantageous drivable exclusively via a gas or air pressure. The additional connection of electricity is neither necessary to operate nor to control the pressure booster, whereby the inventive pressure intensifier can be used particularly advantageous regardless of the respective prevailing voltage in all countries.

Due to the particularly compact summary of the pneumatic unit, hydraulic unit and coupling unit to a handling unit of the inventive pressure intensifier is particularly lightweight, has a particularly short design and is therefore easy to handle and for one person possibly one-handed wearing and / or operated.

The immovable and detachable connection of the hydraulic tool to the hydraulic unit also allows the use of tools in which particularly high forces must be transmitted. These include, for example, punching or riveting tools.

Under an integrally combined handling unit can according to the invention a structural body, for example. A building frame are understood, in which at least the pneumatic, hydraulic and coupling unit fitted and are arranged in connection with each other.

On the other hand, the pneumatic, hydraulic and coupling unit can also form independent assemblies, which, however, are interconnected and possibly interlocked in such a way that they can not be detached from one another during operation of the pressure booster. In addition, the assembled subassemblies are, for example, so interlocked with one another that a functional capability of the one-piece handling unit is given only by the combination of the three subassemblies.

The integrally connected units / assemblies, d. H. the pneumatic, hydraulic and coupling unit and possibly additionally a pressure reducer are, for example, screwed together, pressed or clamped together. As a result, a loosening, separating or a relative movement is prevented from each other during operation, but in the case of maintenance a simple disassembly example. With the help of a disassembly tool allows.

An immovable connection is understood to be a connection in which, in the connected state, if necessary a rotary movement about a common axis, however, otherwise, no relative movement between the coupling unit and the hydraulic tool is possible. The connection is thus designed such that the connection between the coupling unit and the hydraulic tool is rigid and the coupling unit and the hydraulic tool are immovably connected relative to each other. The immovable connection is advantageous because it allows a particularly strong and secure bond between pressure booster and hydraulic tool, which in a particularly advantageous manner, a connection is achieved, record the particularly high workloads or can generate by the pressure booster on the hydraulic tool.

However, the connection between the hydraulic tool and the coupling unit and thus also the handling unit is solvable in any case, in particular easily and quickly detachable, whereby a speedy - possibly even more frequent - change of the hydraulic tool on the pressure booster is made possible.

According to the invention, the coupling unit is adjustable between an unlocking position and a locking position, wherein in the unlocking position the hydraulic tool is separable from or connectable to the coupling unit and in the locking position the hydraulic tool is fixed relative to the coupling unit.

The coupling unit or individual components of the coupling unit can thus assume different relative positions (position) on the handling unit. In addition to the unlocking and locking position, this can be more layers. The adjustment can be made due to different movements. For example. sliding, latching, rotating or deflecting movements are possible for adjustment.

In the unlocking position, a hydraulic tool can be connected to or removed from the coupling unit. In the locking position, however, the hydraulic tool is immovably connected to the coupling unit with this. A relative movement of the hydraulic tool to the coupling unit is therefore not possible in the locking position, apart from possibly a rotational movement about a common axis.

For a change of the hydraulic tool, an adjustment of the coupling unit in the unlocking position is necessary. For safety reasons, the operation of the connected hydraulic tool is only possible in the locking position. As a result, the erroneous use of the unlocked hydraulic tool and an associated high risk of injury of the user is advantageously prevented.

The coupling unit has at least one adjustable between a unlocking position and a locking position locking element as a ball detent body and at least one adjustable between a closure position and an open position blocking element fixing, wherein the locking element fixation in the closed position fixes the blocking element in the locking position and in the open position, the blocking element between the unlocking and the locking position is adjustable.

The blocking element is designed to block the hydraulic tool coupled to the coupling unit.

The adjusting element is adjustable between at least two positions, the unlocking position and the locking position, with an adjustable preference being given to a forward and backward or backward movement of the blocking element. As a result, in particular with respect to removable or plug-in locking elements significantly higher safety and a significantly increased ease of operation is achieved.

The locking element fixing is designed such that it immovably fixes the blocking element in at least one position, wherein immovably a positional fixation of the blocking element with respect to the coupling unit is understood. However, embodiments (for example detent ball elements) are also possible in which a relative movement of the locking elements fixed by the blocking element fixing is possible.

The blocking element fixation can be designed as desired and, for example, engage in the blocking element or attack on the blocking element. The locking element fixing is as well as the locking element between at least two positions, a closure position and an open position, adjustable. The blocking element fixing can, for example, be infinitely or in stages movable.

According to the invention, the coupling unit has a ball latch. At the ball latching in particular designed as a rotatable locking ring, adjustable between the open position and the closure position by turning the locking ring Sperrelementfixierung and a coupling ring coaxially, wherein between an inner side of the locking ring and an outer side of the coupling ring designed to receive the ball detent cavity is formed and the coupling ring has an opening with a smaller diameter relative to the ball detent element and the detent ring has a recess for at least partially receiving the ball detent element, the detent ring, the ball detent element and the coupling ring being matched to one another such that in the closure position the ball detent element is arranged in sections in the aperture is and protrudes from an inner side of the coupling ring and the locking ring in this locking position is secured in position and in the open position, the ball detent element is displaced into the unlocking position.

Under a locking ring is an annular locking element fixing understood. This may have a round cross section, but is preferably formed with a polygonal, in particular a rectangular cross section. The locking ring is preferably rotatably mounted on a coaxial path about a liquid outlet opening. For better handling, he can, for example. On on its outside z. B. grip elements or on its surface gripping structures.

The coupling ring is also formed concentrically to the locking ring, but preferably arranged non-rotatably on the coupling unit. In cross-section, it is like the locking ring also preferably rectangular shaped, but may also have other, especially polygonal shapes.

The openings in the coupling ring are adapted to the shape of the locking elements. In particular, they have a round cross section and are, for example, at least slightly conical on the outside facing the cavity. The openings are also adapted in size to the locking elements. In the case of spherical detent elements, the diameter of the openings is smaller than the diameter of the detent elements and is designed in such a way that the ball lying in the opening projects from the inside of the coupling ring opposite the outside.

For coupling a hydraulic tool to the coupling unit, a coupling element corresponding to the coupling unit is formed on the hydraulic tool. This is preferably also annular and has a matched to the inner diameter of the coupling ring outer diameter. Further, adapted to the locking elements openings or bulges are arranged on the coupling element.

The coupling unit and the coupling element corresponding thereto are thus designed and cooperating in such a way that in the closed position of the blocking element fixing, the blocking elements engage through the openings of the coupling ring into the openings / protrusions of the coupling element, whereby the immovable connection of the hydraulic tool is effected on the hydraulic unit.

By the above-described interaction of locking ring, coupling ring and ball detent body is a particularly simple design and thus insensitive Kugelverrastung realized that produces a particularly strong and rigid connection that can accommodate high workloads and is particularly low maintenance. Furthermore, a fast and frequent tool change is made possible by the particularly simple handling of Kugelverrastung. As a result, manufacturing steps carried out in the production with the pressure intensifier can advantageously be carried out particularly quickly and particularly rationally.

To operate the hydraulic tool connected to the pressure booster, it is necessary to press hydraulic fluid from the pressure booster into the hydraulic tool. For this purpose, according to a development of the invention, the coupling unit has at least one liquid outlet opening which can be closed with an outlet valve and connected to a liquid channel.

Under a fluid channel in this sense is to be understood by the handling unit leading "way" for the liquid. D. h., The channel may be formed from a separate structure, eg. A hose or pipe and / or it is formed of successive spaces of other structures, which are liquid-tightly interconnected.

The fluid channel may have various configurations. For example. For example, the channel may have different cross-sections or different cross-sectional shapes over its length, such as round, oval or polygonal shapes. Also, other structures, such as. Check valves or liquid reservoirs may be arranged in the liquid channel. The liquid outlet opening is preferably formed corresponding to a liquid inlet opening on the hydraulic tool. In particular, round channels or openings are arranged here.

At the liquid outlet opening an outlet valve is arranged. The valve is designed to close the liquid outlet opening and prevents the escape of Liquid from the liquid outlet opening, for example. When changing tools. The opening of the outlet valve can, for example, be done manually for testing purposes or by a hydraulic ram arranged on the opening valve, which acts on the outlet valve, the outlet valve, for example, shifts and so the liquid outlet opening is free, so that the liquid from the liquid outlet opening can flow into the hydraulic tool ,

The outlet valve is arranged in particular in such a way that, when the hydraulic tool is not connected to the coupling unit, it prevents the liquid from escaping from the liquid outlet opening. For this purpose, for example, an outlet valve which presses the outlet valve against a closing edge of the outlet opening is arranged on the outlet valve. An unintentional leakage of the hydraulic fluid, for example. When changing tools or when storing the pressure booster can thus be prevented in an advantageous manner.

According to one embodiment of the invention, the hydraulic unit has at least one flexibly formed liquid reservoir and / or a pump piston working space, which is connected to the liquid reservoir via a suction valve and / or a liquid channel leading from the pump piston working space to the coupling unit and / or a liquid recycling unit having a liquid recycling channel having a first end connected to the liquid reservoir and a second end connected to the liquid channel and / or a movable closure body, which is adapted to redirect the liquid flow in the liquid channel in the liquid return passage on.

Flexible in this sense is understood to be a soft, movable, for example deformable reservoir. This can be formed, for example, from a rubber or plastic material. As a material are in particular with respect to the hydraulic fluid and in particular hydraulic oil, resistant materials.

The liquid reservoir is connected to a pump piston working space. The pump piston working space is designed so that the piston of a pump moves back and forth in this. In operation, the piston of the pump acts on that in the working space Liquid and pushes / pumps them in the liquid channel. Between the pump piston working space and liquid channel, a check valve is also preferably arranged, which prevents the backflow of the liquid from the liquid passage into the pump piston working space during the backward movement of the pump piston.

In order to prevent the occurrence of a vacuum in the pump piston working space during operation by the backward movement of the pump piston, this is connected via an intake valve, which is formed, for example. As a check valve, with the liquid reservoir. The suction valve is designed such that it acts counter to the check valve. That is, as the pump piston slides out of the pumping piston working space, it allows fluid to flow in from the fluid reservoir and closes into the pumping piston working space upon retraction of the pumping piston to prevent ingress of the fluid from the pumping piston working space into the fluid reservoir.

The fluid return unit is configured to return the fluid that has entered the hydraulic tool into the fluid reservoir. In particular, before the hydraulic tool is uncoupled, the fluid in the hydraulic tool should be returned to the fluid reservoir in order to prevent the fluid from escaping from the pressure booster / hydraulic tool. The fluid recycling channel designed for this purpose can be formed and shaped as desired both in the transverse and in the longitudinal direction as well as the liquid channel.

The movable closure body is preferably designed such that in a first position (closure position) it closes the fluid return passage and possibly does not impair the free passage of the fluid through the fluid passage. In a second position, the closure body opens the fluid return passage. In this case, a closure rod embodied as a closure body can be designed and arranged in such a way that it enables exclusively the return of the liquid located in the hydraulic tool and / or in the area of the liquid outlet opening into the liquid reservoir. Alternatively, the closure body in its open position also allow a deflection of the liquid flow, so that both the liquid located in the hydraulic tool and in the region of the liquid outlet opening and the liquid pumped from the liquid reservoir are guided back into the liquid reservoir becomes. As a result, it is, for example, possible that, even in the case of an accidentally triggered pumping movement of the pump piston, the fluid pumped thereby into the fluid channel is returned to the fluid reservoir.

The closure body is preferably equipped with a lever which can be manually actuated by a user of the pressure booster and which shifts the closure body from a first position (closure position) to a second position (opening position). For this purpose, the closure body can, for example, be mounted on a spring in order to return to its closing position when the lever is relieved.

In order to achieve a particularly secure closure of the liquid return channel, the closure body preferably has a conically shaped closure section which is designed to engage in and close an opening of the liquid return channel.

According to a development of the invention, the pneumatic unit has a cylinder unit with a piston working space and a piston unit, wherein the piston unit has a working piston which can be adjusted from a starting position to an end position and the working piston has at least one ventilation duct passing through the working piston and / or a spring-loaded, from a closing piston. in an open position adjustable control piston, which is designed to open the venting channel or close and / or a supply channel, which is connected at a first end to a working space of the control piston, on.

The piston working space is preferably formed by a cylinder housing of the cylinder unit. The piston unit is disposed in the piston working space and adapted to move back and forth between two positions, the home position and the end position. For this purpose, a motion guide of the piston unit preferably takes place on an inner wall of the cylinder housing.

In order to move the piston unit from a starting position to the end position, compressed air is introduced into the piston working space, for example. As a result, a displacement of the piston unit takes place in the piston working space and arises on a first side of the Piston unit a pressurized first part of the piston working space. With the reaching of the end position of the piston working space is divided into a first pressurized part and a second possibly almost unpressurized part.

In order to bring about a return of the piston unit to its starting position, the piston unit is pressurized by a spring. In order for the spring to push the piston back, the pressurized first part of the working space must be relieved. For this purpose, a vent channel is arranged in the piston unit, which connects the first part with the second part of the piston working space.

The vent channel may be formed and shaped according to the liquid channel. It is closed in the initial position of the piston unit with a first end by the spring-loaded control piston, which is adjustable between a closed or open position, on the side of the pressurized first part of the piston unit. With a second end of the vent passage is connected to the second part of the piston working space.

To relax the pressurized first part of the piston working space and to allow the return of the piston unit to the starting position, the control piston is opened during operation, so that the pressure in the pressurized first part can escape through the vent channel and the spring pressure loaded piston unit is pushed back to its original position ,

The control piston is, for example, executable as a valve, but is preferably also designed as a piston-cylinder unit. The spool is adapted to be moved back and forth in a spool work space to open or close the vent passage. Furthermore, a feed channel which opens into the control piston working space at one end is formed, which advantageously allows the inflow of a medium, for example air pressure, into the control piston working space.

Particularly preferably, at least one bypass channel is formed in the cylinder unit. This can be arbitrarily shaped and formed as the fluid channels, but Favor is preferred as a recess, circumferential groove or bore in a cylinder wall of the cylinder unit produced. The bypass passage is connected to the supply passage of the spool working space and allows, depending on the position of the piston unit in the piston working space, the inflow of, for example, compressed air from the first part of the piston working space into the control piston working space.

The bypass channel is preferably arranged such that it is opened to the first part of the piston working chamber only when the piston unit is at least approximately in the end position. The connection to the supply channel may be permanent or also opened depending on the position of the piston unit in the piston working space. This makes it possible in an advantageous manner to relax the pressurized first part of the working space, whereby the piston unit can be particularly easily returned from its final position to its original position.

According to a development of the invention, the pneumatic unit has a pump unit, with a connected to the piston unit, adjustable between a starting position and an end position, reaching into the hydraulic unit pump piston and connected to the pump piston compression spring, which is adapted to a pressing pressure on the piston unit exercise.

The connection between the pump piston and the piston unit can, for example. Force and / or positive fit. Thus, for example, it is possible that the pump piston and the piston unit are arranged with only two surfaces together. Also gears between the pump piston and piston unit are possible, which produce a composite, for example. A relatively immovable composite. Due to the bond between piston unit and pump piston, the pump piston moves with a movement of the piston unit. The pump piston is therefore adjustable as the piston unit from a starting position to an end position.

The pump piston can, for example, be designed as a ram. Preferably, it is adapted in shape and dimension to the inner wall of the pump piston working space and designed such that it slides back and forth in the pump piston working space.

The piston unit is - as already described - pressurized by a spring, the allowing the piston unit to be returned to its starting position. The compression spring can be designed such that it acts, for example, on a front side of a base plate of the pump piston, wherein the front side of the opposite rear side of the base plate is in contact with the piston unit.

As a result, it is structurally possible in a particularly simple manner to return both the piston unit and the pump piston to the starting position with a compression spring.

According to one embodiment of the invention, the pneumatic unit on at least one compressed air supply unit, the at least one for adjusting a gas or air volume flowing into the pneumatic unit formed flow control valve and / or a gas or air supply channel occlusive opening valve and / or a pressure reducer for setting a in the Pneumatic unit incoming gas or air pressure which is integrally formed with the handling device comprises.

To set the operating speed of the pressure booster, a flow control valve is formed on the compressed air supply unit. This is adjustable, for example. Screw-arranged and can change the volume of the supplied compressed air. About the volume change of the working stroke (working speed) of the pneumatic unit is regulated. The flow control valve is, for example, designed such that it engages in the inlet opening of a gas or air supply duct and increases or reduces its cross-section.

The preferably arranged opening valve serves to open a gas and air supply channel and thus also to control the pressure booster. The opening valve allows the gas or air supply to be switched on or off in the pneumatic unit. The opening valve is preferably designed so that it enters the pneumatic unit in the opening position air / gas, whereby the pneumatic unit can begin its duty cycle and locked in the closed position the gas or air supply passage, so that no work is performed in the pressure booster.

The opening valve is preferably operable with a lever operable by the user of the pressure booster. This is a particularly simple and manual operation of the portable intensifier by the user.

The pressure reducer serves to regulate the inlet pressure of the inflowing medium into the pneumatic unit. The intensifier boosts the inlet pressure via its pneumatic-hydraulic system. For example, translations from 1:50 to 1: 100, possibly up to 1: 200, are possible. At a high input pressure, a particularly high output pressure is generated accordingly. For example. Depending on the size of the intensifier, ratios below 1:50 or above 1: 200 are possible. The efficiency of the pressure reducer is preferably between 75% to 90%, advantageously between 80% to 85%.

Particularly preferably, the pressure booster is operated with an inlet pressure of 2-16 bar, preferably with a working pressure of 6 bar. In order to enable the greatest possible independence of the intensifier from external devices, the pressure reducer is formed integrally with the handling unit. Integral in this sense is to be understood in accordance with the pre-defined integral nature of the handling unit.

According to one embodiment of the invention, the handling unit has a weight between 0.5 kg and 10 kg, preferably between 0.75 kg and 6 kg, more preferably between 1.0 kg and 4 kg, advantageously between 1.25 kg and 2.5 kg and preferably between 1.5 kg and 2.25 kg, and / or a length between 120 mm and 400 mm, preferably between 140 mm between 350 mm, particularly preferably between 160 mm and 300 mm, advantageously between 180 mm and 275 mm and preferably and 200 mm between 250 mm.

The particular advantage of the low weight and / or the short length is the special mobility and portability of the pressure booster. Due to the low weight, a single user can use the intensifier particularly easily. Possibly. even one-handed use is possible.

The particularly short length of the handling unit also allows the user easy handling and the use of pressure intensifier or one with the hydraulic intensifier used hydraulic pressure in particularly narrow areas of manufacture.

Another application, which is advantageously made possible in particular due to the low weight and the short length of the handling unit, is, for example, the use of the handling unit in the field of body scissors or body splitter for rescue operations.

Fig. 1

einen schematischen Querschnitt einer Ausführungsform des erfinderischen Druckübersetzers;

Fig. 2

einen schematischen Querschnitt einer Kopplungseinheit und einer Flüssigkeitsrückführungseinheit aus Figur 1;

Fig. 3

einen schematischen Querschnitt einer Handhabungseinheit aus Figur 1, mit einem Arbeitskolben in einer Ausgangsposition;

Fig. 4

einen schematischen Querschnitt einer Handhabungseinheit aus Figur 1, mit einem Arbeitskolben in einer Endposition;

Fig. 5

einen schematischen Querschnitt einer Handhabungseinheit aus Figur 1, mit einem geöffneten Steuerkolben;

Fig. 6

einen schematischen Querschnitt einer Handhabungseinheit aus Figur 1, mit einem Arbeitskolben in einer rückführenden Position;

Fig. 7

einen schematisch dargestellten Querschnitt durch eine Kopplungseinheit aus Fig. 1.

In the following, embodiments of the invention will be explained in more detail with reference to figures. In the figures show:

Fig. 1

a schematic cross section of an embodiment of the inventive pressure intensifier;

Fig. 2

a schematic cross section of a coupling unit and a liquid recycling unit FIG. 1 ;

Fig. 3

a schematic cross section of a handling unit FIG. 1 with a working piston in a starting position;

Fig. 4

a schematic cross section of a handling unit FIG. 1 with a working piston in an end position;

Fig. 5

a schematic cross section of a handling unit FIG. 1 , with an open control piston;

Fig. 6

a schematic cross section of a handling unit FIG. 1 with a working piston in a recirculating position;

Fig. 7

a schematically illustrated cross section through a coupling unit Fig. 1 ,

FIG. 1 shows an embodiment of a pressure intensifier 1 according to the invention with a handling unit 2, which consists of a coupling unit 3, a hydraulic unit 4 and a pneumatic unit 5. Further, an integrally formed with the handling unit 2 pressure reducer 6 and not connected to the pressure booster hydraulic tool 7, which has a coupling unit 3 corresponding to the coupling element 8, shown.

The pressure booster 1 is circular in cross-section and, together with the pressure reducer 6 has a length of 275 mm +/- 10 mm and a weight of about 2 kg +/- 200 g. An alternative without pressure reducer 6 trained pressure booster 1 has a length of 220 mm +/- 10 mm and a weight of 1.8 kg +/- 200 g.

At the pressure reducer 6 is a compressed air connection 9, which is connected to an air supply passage 10 is formed. The air supply duct 10 leads through the pressure reducer 6 via a flow control valve 11 and via an opening valve 12 into a piston working space 13 of a cylinder unit 13a. The pressure reducer 6, the air supply passage 10, the flow control valve 11 and the opening valve 12 are part of the compressed air supply unit 6b.

The flow control valve 11 is formed as a cylindrically shaped valve for screwing. A first end of the flow control valve 11 is designed as a handle. A second end of the flow control valve 11 is tapered and conically shaped and arranged in a passage channel 15 of the air supply passage 10. By screwing in or unscrewing the flow control valve 11, the opening cross-section of the passage channel 15 can be influenced, whereby the penetrating into the piston working space 13 air volume can be regulated.

The opening valve 12 is resiliently mounted and designed to close the air supply passage 10 with a conical valve seat 12a. The opening valve 12 is displaceable against the spring force via a lever 12b arranged on the opening valve 12, so that the conically shaped valve seat 12a opens the air supply duct 10 and the compressed air can flow through the air supply duct 10 into the piston working chamber 13. The lever 12 b is surrounded by a protective bracket 12 c to prevent inadvertent opening of the opening valve 12 in use.

The cylinder unit 13a has a cylinder housing 13b which encloses the piston working chamber 13 of a working piston 14. The working piston 14 is movable back and forth in operation between a starting position and an end position. Shown is the working piston 14 in the end position. The piston working space 13 is through the working piston 14 in a first part 16, in which the air supply channel 10 opens and which can be acted upon with compressed air and a second part 17 separated.

The working piston 14 is constructed of several structures and corresponds to the piston unit (not designated here). It has a working surface 18, which is aligned with the first part 16 of the piston working chamber 13, and a connecting surface 19, which is aligned with the second part 17 of the piston working space 13. On the working surface 18, a valve extending in the working piston 14 is arranged, designed here as a control piston 20 with a control piston working chamber 21. The control piston 20 is mounted on a compression spring and in its Steuerkolbenarbeitsraum 21 back and forth movable. The control piston 20 closes a ventilation channel 22 arranged below the working surface 18, which connects the first part 16 to the second part 17 of the piston working chamber 13.

Viewed in the direction of movement of the working piston 14, its outer diameter varies. While it rests in each case in the region of the working surface 18 and the connecting surface 19 on an inner side 13c of the cylinder housing 13b, the cross section is slightly smaller in a region between these contact surfaces, so that an air duct 23 coaxially surrounding the working piston 14 is formed.

The air channel 23 is arranged on the one hand with a supply piston 49 which is arranged in the working piston 14 and connects the air channel 23 with the control piston working chamber 21 (see FIG. Fig.3-6 ) connected. On the other hand, the air channel 23 communicates with a bypass channel 25 arranged in the inner side 13c of the cylinder housing 13b. The supply channel 49 is formed as a bore in the working piston 14, the bypass channel 25 as on the inner side 13c of the cylinder housing 13b circumferential recess.

The bypass passage 25 is disposed on the inner side 13 c such that in the end position of the working piston 14, an outer end (the working surface 18) of the working piston 14 is disposed above the bypass passage 25 and the bypass passage 25 is in addition to the air passage 23 with the first part 16 the piston working space 13 is connected.

As a result, in the end position (or already in the region shortly before reaching the end position) of the working piston 14, a flow from the first part 16 of the piston working space 13 through the bypass channel 25, the air channel 23 and the supply channel 49 in the control piston working space 21 possible.

Furthermore, the shows FIG. 1 one on the connecting surface 19 of the working piston 14 arranged pump piston 26. The pump piston 26 has a base plate 27 which bears against the connecting surface 19 of the working piston 14.

The pump piston 26 is mounted in the second part 17 of the piston working space 13 in a guide 28. With one of the base plate 27 opposite end of the pump piston 26 engages in the hydraulic unit 4 and here in a pump piston working chamber 29 a. To the guide 28, a compression spring 30 is arranged, which rests on the base plate 27 and thus exerts a pressure on the working piston 14.

Further, a pump piston housing 50 enclosing the pump piston working space 29 is arranged. The pump piston housing 50 is designed as a guide for the pump piston 26.

In the hydraulic unit 4, a liquid reservoir 32 enclosing a rubber membrane 31 is arranged. The liquid reservoir 32 is connected to the pump piston working chamber 29 via a suction valve 33 arranged in the pump piston housing 50.

From the pump piston working chamber 29, a fluid channel 34 leads to the coupling unit 3. The fluid channel 34 ends at a fluid outlet opening 35, which is closed by an outlet valve 36.

Immediately following the pumping piston working space 29, the liquid passage 34 is interrupted by a check valve 37, which prevents the backflow of liquid from the hydraulic tool 7 / liquid passage 34 into the pumping piston working space 29.

In the transition region between the hydraulic unit 4 and the coupling unit 3, a liquid recycling unit 38 is arranged. This consists of a closure body 39, which is manually movable via a lever 40 and a fluid return passage 41 which terminates at a first end into the fluid passage 34 and at a second end (not shown) in the fluid reservoir 32.

Fig. 2 shows a section of the coupling unit 3 and the liquid recycling unit 38 from Fig. 1 , The liquid outlet opening 35 is circular in cross section and formed like a nozzle. It is closed by an outlet valve 36 mounted with a spring 42. The outlet valve 36 has a sealing ring 43 in the region of the outlet opening.

The illustrated coupling unit 3 shows a coupling ring 44, which is arranged coaxially with the outlet opening 35. The coupling ring 44 has openings 45 for receiving ball detents (not shown here).

The closure body 39 of the liquid recycling device 38 is mounted with a compression spring 46, which is arranged in the liquid passage 34. The closure body has a trapezoidal switch 47, which closes the liquid return passage 41 in a closed position of the closure body 39. In the open position (not shown here) of the closure body 39 is pressed against the spring force of the compression spring 46, whereby the conical diverter 47, the liquid return passage 41 releases and both the liquid from the liquid passage 34 and the liquid flowing back in the liquid passage 34 from the hydraulic tool ( not shown here) in the liquid return passage 41 deflects.

Fig. 3 shows the working piston 14 in the starting position, which rests with its working surface 18 on a side wall 5a of the pneumatic unit 5. The control piston 20 is in a closed position and closes the venting channel 22 arranged in the working piston 14. The supply channel 49 connects the control piston working chamber 21 to the air duct 23.

The compression spring 30 presses against the voltage applied to the working piston 14 base plate 27 of the pump piston 26.The piston working space 13 of the working piston 14 is formed in the starting position exclusively by the second part 17 of the piston working chamber 13. Of the second part 17 is connected to a muffler, which allows the escape of air from the second part 17 of the piston working chamber 13.

The pump piston 26 is also in its starting position. The pump piston working chamber 29 is filled with liquid, here hydraulic oil. The pump piston working space 29 is formed by a housing 50 sealed off from the liquid reservoir 32. In the housing 50, the suction valve 33 for sucking the liquid from the liquid reservoir 32 into the liquid working space 29 is arranged.

Fig. 4 shows the power piston 14 in its final position. The piston working space 13 is formed by the second part 17 and the air pressure-applied first part 16. In operation, the piston working chamber 21 of the control piston 20 fills via the supply channel 49, the air channel 23 and the bypass channel 25 with compressed air from the first part 16 and pushes the control piston 20 out of the working surface 18 of the working piston 14 (see FIG. 5 ).

As a result, the access between the compressed air-filled first part 16 and the venting channel 22 is opened. The compressed air in the first part 16 escapes through the venting channel 22 into the second part 17, from which it can escape via the muffler 48.

Due to the decreasing pressure in the first part 16 and the force acting on the working piston 14 by the spring 30, the working piston 14 is pushed back into its starting position. In this case, the working piston 14 slides over the bypass channel 25 and closes it, so that no further air from the first part 16 can penetrate via the bypass channel 25 in the piston working chamber 21.

Shortly before reaching the end position of the working piston 14, the control piston 20 is pushed back into the work surface 18 and the vent passage 22 is closed (see FIG. 6 ).

As in FIG. 4 is shown in the end position of the working piston 14 and the pump piston 26 in its final position and has the hydraulic oil from the pump piston working space 29 pushed into the liquid passage 34 and through the check valve 37.

With the backward movement of the working piston 14 and the pump piston 26 is moved back to its original position. This results in the piston working chamber 29, a negative pressure through which the liquid is sucked from the liquid reservoir 32 through the intake valve 33 into the pump piston working chamber 29.

Fig. 7 shows a cross section through a coupling unit with coaxially arranged ball detents 52 and a coupling ring 44. The coupling ring 44 has openings 45 which are closed by the ball detent 52. The ball detent body 52 and the openings 45 in the coupling ring 44 are matched to one another in such a way that the ball detent bodies 52 seated in the openings 45 project from the inside 53 of the coupling ring 44 through the openings 45.

A locking ring 51 is arranged coaxially around the coupling ring 44, so that between the locking ring 51 and the coupling ring 44, a cavity 54 is formed, in which the ball detent body 52 are arranged. The locking ring 51 has on its inner surface 56 at a distance of 45 ° from each other arranged recesses 55. The locking ring 51 is rotatably supported by at least 22.5 °. Alternatively, the distance of the ball detent can also be formed larger or smaller than 45 °, wherein the minimum rotation of the locking ring is adjusted accordingly.

Fig. 7 shows the locking ring 51 in a closed position. The inner surface 56 of the locking ring bears against the ball detent bodies 52 and secures the position of the ball detent body in the opening 45 of the coupling ring 44. To move the detent ring 51 into its open position, it is rotated by 22.5 ° counterclockwise or clockwise. In the opening position, the recesses 55 are above the ball detent body 52, so that they are movable out of the openings 45 into the recesses 55.

Claims (9)

1. A portable pressure transducer (1) for driving exchangeable hydraulic tools (7), having

   - a gas or air pressure driven pneumatic unit (5),

   - a hydraulic unit (4) connected to the pneumatic unit (5),

   - a coupling unit (3) for immovably and releasably connecting the hydraulic tool (7) to the hydraulic unit (4),

   wherein the pneumatic unit (5), the hydraulic unit (4) and the coupling unit (3) are integrated into a one-piece mobile handling unit (2), characterized in that the coupling unit (3) has a spherical catch mechanism, wherein

   - a locking element fixing, which is configured as a twistable locking ring (51) and which can be adjusted between the opening position and the closing position by twisting the locking ring, and a coupling ring (44) are arranged coaxially,

   - there is configured between an inner side of the locking ring (51) and an outer side of the coupling ring (44) a cavity (54) which is configured to receive a locking element which is configured as a spherical latching body (52) and which can be adjusted between an unlocking position and a locking position,

   - the coupling ring (44) has an opening (45) having a smaller diameter compared to the spherical latching body (52),

   - the locking ring (51) has a recess in order to receive at least in sections the spherical latching body (52), and

   - the locking element fixing in the closed position fixes the locking element in the locking position and in the opening position the locking element can be adjusted between the unlocking position and the locking position,

   wherein the locking ring (51), the spherical latching body (52) and the coupling ring (44) are matched to one another such that

   - in the closing position the spherical latching body (52) is arranged in sections in the opening (45) and projects from an inner side (53) of the coupling ring (44) and is secured by the locking ring (51) in this locking position, and

   in the opening position the spherical latching body (52) can be moved into the unlocking position.
2. The portable pressure transducer according to Claim 1, characterized in that the coupling unit (3) can be adjusted between an unlocking position and a locking position, wherein in an unlocking position the hydraulic tool (7) can be separated from the coupling unit (3) or can be connected thereto and in the locking position the hydraulic tool (7) is fixed relative to the coupling unit (3).
3. The portable pressure transducer according to Claim 1, characterized in that the coupling unit (3) has at least one fluid outlet opening (35) which can be closed with an outlet valve (36) and is connected to a fluid channel (34).
4. The portable pressure transducer according to Claim 1, characterized in that the hydraulic unit (4) has at least

   - one flexibly configured fluid reservoir (32), and/or

   - one pump piston work chamber (29) which is connected by means of a suction valve (33) to the fluid reservoir (32), and/or

   - one fluid channel (34) starting from the pump piston work chamber (29) leading to the coupling unit (3), and/or

   - one fluid recirculation unit (38) having a fluid recirculation channel (41) which is connected at a first end to the fluid reservoir (32) and which is connected at a second end to the fluid channel (34), and/or

   - one movable closing body (39) which is configured to deflect the fluid flow in the fluid channel (34) into the fluid recirculation channel (41).
5. The portable pressure transducer according to Claim 1, characterized in that the pneumatic unit (5) has a cylinder unit (13a) having a piston work chamber (13) and a piston unit/working piston (14) which is adjustable from a starting position to an end position, wherein the piston unit/working piston (14) has at least

   - one venting channel (22) penetrating the working piston (14), and/or

   - one spring-loaded control piston (20) which can be adjusted from a closing to an opening position, which control piston is designed to open or close the venting channel (22), and/or

   - one supply channel (49) which is connected at a first end to a work chamber (21) of the control piston (20).
6. The portable pressure transducer according to Claim 1, characterized in that at least one bypass channel (25) is configured in the cylinder unit (13a).
7. The portable pressure transducer according to Claim 1, characterized in that the pneumatic unit (5) has a pump unit, having

   - a pump piston (26) extending into the hydraulic unit (4), which pump piston is connected to a working piston (14) and can be adjusted between a starting position and an end position, and

   - a compression spring (30) connected to the pump piston (26), which compression spring is designed to exert a pressing force on the working piston (14).
8. The portable pressure transducer according to Claim 1, characterized in that the pneumatic unit (5) has at least one pneumatic supply unit (6b) which has at least

   - one flow control valve (11) which is configured to adjust a gas or air volume streaming into the pneumatic unit (5), and/or

   - one opening valve (12) closing a gas or air supply channel, and/or

   - one pressure reducer (6) for adjusting a gas or air pressure streaming into the pneumatic unit (5), which pressure reducer is configured in one piece with the handling unit (2).
9. The portable pressure transducer according to Claim 1, characterized in that the handling unit (2) has

   - a weight between 0.5 kg and 10 kg, preferably between 0.75 kg and 6 kg, particularly preferably between 1.0 kg and 4 kg, advantageously between 1.25 kg and 2.5 kg and preferably between 1.5 kg and 2.25 kg, and/or

   - a length between 120 mm and 400 mm, preferably between 140 mm and 350 mm, particularly preferably between 160 mm and 300 mm, advantageously between 180 mm and 275 mm and preferably between 200 mm and 250 mm.

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