SE1300726A1 - Pump / motor - Google Patents

Abstract

Pump / motor (1) which comprises a housing (2) which comprises at least three cylinder / piston units (3), each comprising at least one cylinder and at least one piston, which are driven by pressurized medium or pressurized medium and that the pump / motor comprises at least one unit (10) for converting rotary motion to reciprocating motion of the pistons in the cylinders or alternatively converting reciprocating motion of the pistons in the cylinders to a rotating motion. The unit (10) for converting rotary movement to reciprocating motion of the pistons in the cylinders, alternatively converting reciprocating motion of the pistons in the cylinders to a rotating motion, is interchangeable, whereby it is possible to adapt the pump / motor to speed.

Description

Technical Field The present invention relates to a variant of a pump / motor in accordance with the claims.

Technical background Throughout the ages, a number of different types of motors and pumps have been developed. A variant of the above-mentioned motors and pumps is slid out of motors / pumps which are driven by pressurized liquid or pressurized liquid. One type of these motors / pumps consists of hydraulic motors / hydraulic pumps.

A problem with existing types of pumps, such as hydraulic pumps, is that these mainly have fixed displacements and that they are intended to be operated within the limited speed range. If there is a need for another displacement, the engine must be replaced or connected to at least one second hydraulic motor, which entails expensive and cumbersome arrangements which usually require a large amount of space.

Furthermore, kanda hydraulic pumps / hydraulic motors with cam curves (cam ring motors) are only substantially law-driven. This is due to a number of different reasons. One of these reasons is that the speed of the cam rollers risks becoming very high, which can cause problems for the few cam roller bearings. A further problem with rotary hydraulic motors of the cam ring type is that these lead to gearboxes and similar requirements if a relatively higher speed is sought. There are no prior art constructions of hydraulic motors / hydraulic pumps which include an integrated shaft function which is not substantially awkward or the like.

A further problem with existing pumps, such as hydraulic pumps, is that the hydraulic pumps are not adapted so that at one time they can be operated at a relatively lower rotational speed and at another time can be operated at a relatively higher rotational speed. Narruida problems are particularly common in the case of available driving cold, have a substantially high rotational speed and have a low speed, respectively. AU satisfies bd. & These needs entail with today's kanda telcnik aft a need for a number of different models of pumps / motors exists. The cost of manufacturing and possibly stocking these variants can thus be high. 2 Another problem with existing constructions of hydraulic motors / hydraulic pumps is that known types of constructions usually in manufacture have a high accuracy with tight tolerances. This is the case, for example, with the processing of cam curves and the like. The tolerance requirements entail a relatively high manufacturing cost for components included in existing motors / pumps.

An additional problem with existing constructions of hydraulic motors / hydraulic pumps is that the surface pressure on the line rollers must not exceed a certain level, value. This means that the hydraulic motors can preferably only have an input control pressure on the oil, which is limiting.

A further problem with existing types of hydraulic motors / hydraulic pumps which these usually only include hydraulic cylinders (cylinder piston units) which are single acting. This results in the constructions of the hydraulic motors becoming rather large and awkward when compared with the construction in accordance with the present invention. Designs to reduce the size of the motor / pump have been developed which use double cam curves. The major problem with known constructions of motors / pumps with double cam curves is that these may require a rotational change of the cam rollers when a change of the drive of the cam rollers from the outer cam curve to the inner cam curve occurs. The construction can also mean that the distance between the cam curves must be stone and the diameter of the cat rollers few function can be obtained, which in turn results in a gap between the rollers and the cam curves.

KAnd technology Over time, a large number of hydraulic motors / hydraulic pumps have been developed. An example of a hydraulic motor which comprises double-acting cylinders is a construction which is described in the patent specification US8252401. The construction in accordance with the patent specification US8252401 otherwise differs to a large extent in relation to the construction in accordance with the present patent. For example, the construction according to patent application US8252401 does not comprise a replaceable unit with which the properties of the engine can be changed.

The Swedish patent application SE1300146-6 of applicant, which has not yet been published, describes a variant of a hydraulic motor / hydraulic pump which uses double-acting cylinders. However, the construction according to the patent specification differs from the construction in accordance with the present invention. For example, it is not possible to adapt the structure 3 to be driven by drive units with different speeds. The construction further does not comprise a replaceable shaft unit, which allows the construction to be adapted to high or set speeds.

The Swedish patent application SE describes a variant of a hydraulic motor / hydraulic pump which comprises an eccentric which drives a plurality of cylinder / piston units. The construction is made up of modules of cylinder / piston units. However, the construction according to patent application SE differs in significant extent from the construction in accordance with the present patent application. For example, it is not possible to adapt the design to be driven by drives with different speeds. The construction further does not comprise a replaceable shaft unit, which allows the construction to be adapted to high or set speeds.

Although developed pumps and motors usually fulfill their intended purposes, there are still a number of problems with the known motors and pumps.

The main object of the present invention The main object of the present invention is to create a pre-fitted motor / pump which solves or reduces at least one of the above-mentioned problems. The unit is achieved with a hydraulic motor / hydraulic pump in accordance with the claims.

Brief Description of the Figures The invention will be further described in the following detailed description with reference to the accompanying schematic drawings which, by way of example, show the presently preferred embodiments of the invention.

Figures 1A and 1B show a first embodiment of the present hydraulic motor which in Figure 1A is seen from the fium side and in Figure 1B is seen in radial direction.

Figures 2A and 2B show a cross-section, end removed, of the first embodiment of the present hydraulic motor.

Figures 3A to 3D show the second embodiment of the pump / motor in accordance with the present patent application.

Figures 4A and 4B show the body with associated cylinder piston units. Figure 5A shows a replaceable center part for use at high speed. Figure 5B shows a second variant of center part for use at set speed.

Figure 6 shows a hydraulic diagram.

Figures 7A and 7B show an exemplary cylinder / piston unit. Figures 8A and 8B show the shaft in detail in Figures 7A and 7B in more detail. Figure 9 shows in a cross section of the pump / motor in its axial direction.

Figure 10 shows an alternative embodiment of the pump / motor which includes both an eccentric and a corneal curve.

Figure 11 shows a variant of cylinder / piston unit.

Figure 12 shows an embodiment where the cannons consist of segments. Detailed description of the invention With reference to the figures, a pump 1, alternatively motor, is shown in accordance with the present patent application. The pump (motor) 1 comprises at least one housing 2, body 3 or similar saint at least one unit which transmits rotating motion to or from the pump / motor. The unit for transmitting rotating motion to or from the pump / motor is in the exemplary embodiment of a shaft 4. When the construction works as a pump, the shaft 4 constitutes an input shaft and when the structure acts as a motor, the shaft 4 constitutes an output shaft. The unit for transmitting rotating motion to or from the pump / motor can in alternative embodiments be constituted by the housing, the storm or the like.

As a pump, this is intended to pump any type of liquid such as hydraulic oil, water or other types of water shoes which the pump can pump. It is also conceivable that the pump pressurizes gas or gases. As an engine, it can be driven by any type of fluid such as hydraulic oil, water or other water shoes with which the engine can be driven. It is also conceivable for the engine to be operated with pressurized gas or pressurized gases.

In the exemplary embodiments, the housing 2 preferably comprises at least one frame 3, saint at least one end 5 and in the exemplary embodiment at least one first end 5 and at least one second end 6. In alternative embodiments, at least one end 5 or 6, or the ends 5 and 6, be integrated in the housing 2, the frame 3 or the like.

The construction preferably comprises a plurality of cylinder / piston units 7, each of which comprises at least one cylinder (cylinder unit) 8 and at least one piston 9 (shown, for example, in Figure 2 and in Figures 5B and 5C). In alternative embodiments, the number of cylinder / piston units is at least three. In further alternative embodiments, the number of cylinder / piston units may be less than three.

Unique to the present invention is that the properties of the pump can be different so that it can be operated with a relatively lower rotational speed and a relatively higher rotational speed. The various properties are achieved by a replaceable unit (the shaft unit and the unit for converting rotary movement into a reciprocating movement of the piston 9 in the cylinder 8). Referring to Figure 2, a first of the pump / motor 1 configurations is shown. Referring to Figure 3, a second configuration of the pump / motor 1 is shown.

Referring to Figures 2A - 2G, a first configuration of the pump / motor 1 is shown. In the first embodiment of the replaceable unit 10, the conversion of the rotated motion to the forward and reciprocating motions of the cylinders 8 of at least one first cam curve 11 the replaceable unit 10 therefore comprises at least a first cam curve 11 which via cam rollers 12 or the like controls the reciprocating movement of the pistons 9 in the cylinders 8. In a preferred embodiment the construction comprises at least a first inner cam curve 11 and at least an outer cam curve 13 or the like, controls the reciprocating movement of the pistons 9 in the cylinders 8. Figure 2D shows an embodiment which comprises at least a first inner (in radial direction) cam curve 11 and at least a first outer (in radial direction) cam curve 13 and further at least a second inner cam curve 14 and at least one second outer cam curve 15. At least one of the cam curves may in alternative embodiments be built up of s elements 16 which are compound (together) form the cam curve. Aft builds the cam curve of segments facilitates, and reduces material supply, during production.

Referring to Figures 3A and 3B, an exemplary embodiment of the replaceable unit 10 is shown where it is intended to be driven by a drive unit having a relatively 'Ogre speed', or to operate something at a relatively higher speed, than the unit in accordance with the first configuration. In the form of configuration (configuration) of the replaceable unit 10 shown in the figure, this comprises at least one eccentric 17 which, via at least one transfer device 18, transfers the eccentric 17 in the radial direction to the piston 9 or the pistons 9.

During a rotation of the shaft 4 with associated eccentrics 17, alternatively connected eccentrics 17, the pistons 9 are influenced to perform a reciprocating movement in the cylinders 8. The eccentrics 17 in 6 the replaceable unit 10 can have different shapes. In alternative embodiments, the eccentric 17 can be interchangeable in relation to the shaft.

In the exemplary embodiment shown in Figures 3A and 3B, a transfer device 18 is shown which comprises an annular part 19. The annular part 19 preferably comprises a circular hall in its center. The edge of the circular Met is affected by the eccentric. During a rotation of the shaft with associated eccentrics, the eccentric influences the annular part to be layered in the radial direction in a corresponding manner as the eccentric. The transfer device comprises push rods which are connected to the radially outer part of the annular part. The push rods 20 or the like are in one end mounted connected via connecting means 21 to the annular part 19. The push rods 20 are in their other end preferably mounted connected to the shaft 22, where the cam rollers 13 are connected in the previously described embodiment with one or more cam curves in in accordance with Figures 2A and 2B.

During a rotation of the shaft 4 with associated eccentrics 17, the pistons 9 are influenced by the pressure rods 20 to perform a reciprocating movement in the cylinders 8. The annular part outer diameter can vary within the scope of the invention.

Referring to Figures 4A - 4b, the body 2 is shown with the associated cylinder / piston units 23. The body comprises at least three cylinder / piston units 23 and preferably a plurality of cylinder / piston units 23. The cylinder / piston units 23 are shown in more detail in Figure 5 and are described in more detail in the accompanying description. Stonunen 2 is four times stationary during operation. In alternative embodiments it is conceivable that the body 2 rotates and that the replaceable part (center part) 10 is stationary. There may be embodiments where the replaceable part (center part) 10 and the body 2 both rotate. In the exemplary embodiment, the body comprises 2 channels for supply of liquids / water shoes or gas / gases as well as connections for suction lines and return lines and further construction details obvious to the person skilled in the art.

Referring to Figures 5A to 5C, an exemplary embodiment of the cylinder / piston assembly 23 with associated components is shown. The exemplary cylinder / piston unit 23 is not limiting of the inventive concept of the present pump / motor 1 design. The cylinder / piston unit 23 comprises at least one cylinder housing 24 at least one shaft 25 with connected piston 9. The cylinder / piston unit comprises at least one guide 26 for controlling the movement of the cam roller in the axial direction of the cylinders. Referring to Figure 5B, a cross-section of the cylinder / piston assembly 23 is shown in its axial direction. The figure shows the shaft 25 with associated bearings. Figure 5B also shows how the cylinder / piston unit 23 preferably comprises replaceable liner 27. By replacing the liner 27 and the piston 9, the displacement of the cylinder / piston unit 23 can change.

Figure 5B, shown in Figure 5C, shows that the shaft comprises at least one first cam roller (wheel) 12 which is intended to run against at least one first cam curve. The construction preferably comprises at least one second cam roller (wheel) 12 which is intended to run against (abut against) at least one second cam curve.

In the exemplary embodiment, the construction comprises at least one first cam roller (wheel) 12 which is intended to run against at least one first inner cam curve and at least one second cam roller (wheel) 12 which is intended to run against (abut) at least one second cam curve and at least one fourth cam roller intended for loops against at least one fourth cam curve. The cam rollers and cam rings may be conical in axial direction. The conical cam rollers are intended to abut against cam curves which are angled. The angle of the conical rollers and the windings of the core curves are adapted in relation to each other so that these obtain a satisfactory function with the conical core rollers.

Figures 5B and 5C also show that the piston rod is mounted to the shaft via at least one early roller bearing 28. The figures show ay bearing 29, as preferably customs bearings, which bear the shaft 25 in relation to the guides 26. The construction causes breaks against the piston rod is reduced. The construction with a separate bearing allows the shaft to be tilted, which allows stone tolerances to existing types of pumps / motors. This is made possible by the aft shaft being stored relative to the piston ladder, with at least one spherical bearing.

Through the construction, the movement of the piston in one radial direction is controlled by the first and the second cam curves. In the opposite radial direction, the piston is guided by the third cam curve and the fourth cam curve.

Figure 5B also shows a cylinder 8 with associated piston 9. The piston 9 divides the cylinder 8 into at least one first chamber (A side) and at least one second chamber 31 whose pressurization is controlled by at least one control system. The figure also shows fittings connected to the lining. In the exemplary embodiment, the structure comprises at least one cavity (chamber) 32 which can absorb lacquer of pressurized medium. The hall space 32 is connected to the low-pressure side (inflow). Unique to the present pump / motor construction is that it includes a function by which the force with which the piston acts on the cam rollers can be controlled. By controlling the force, it is possible to regulate the surface pressure between the cam rollers and the cam curves.

Referring to Figure 6, an exemplary construction is shown in a hydraulic diagram with which a control of the force acting on the cam rollers takes place. The figure shows a cylinder 8 with associated piston 9. The piston 9 divides the cylinder 8 into at least one first chamber (A side) 30 and at least one second chamber (B side) 31. The construction further comprises at least one valve 33 which controls the inflow to chamber 30. (A side) and at least one valve 34 which controls the inflow to chamber 31 (B side). The construction comprises a valve which opens and closes at least one channel which connects chamber 30 (A side) and chamber 31 (B side).

By re-activating the valves 33 to 35 in different ways, at least three different maximum pressures between the cam roller and cam curve can be achieved (in addition to the shut-off valve). By aft control if each valve is open or closed, an adjustment of pressure and flow can take place.

If valve 33 on the A side is activated, the volume is used in chamber 30 (A side) in the cylinder.

If valve 34 is activated, the volume is used in chamber 31 (B side) in the cylinder.

Mr valves 33, 34 and 35 are activated so the volume is used which is the difference between chamber 30 (A side) in the cylinder and chamber 31 (B side) in the cylinder, which corresponds to the volume of the piston rod in the cylinder.

When applying oil pressure, the above alternatives 1 to 3 can be used. At medium pressure, alternatives 2 and 3 are used. At high pressure, alternative 3 is used. When the pressure has reached the maximum level, valves A and B are opened, which means that the cylinder does not push anything out on the high-pressure side. The pump thus does not pump out the oil to the high-pressure side, but the oil returns to the tank (low-pressure side).

With the construction, the hydraulic pressure can vary without the maximum surface pressure (critical surface pressure) on the cam roller surface being exceeded.

In alternative embodiments, the construction comprises pressure sensors at channels to the A side and the B side, respectively. By processing data from the pressure sensors, the status of the cylinder can be analyzed so that the output power and input power, respectively, are calculated and controlled. 9 With this control, you can control and find out the power that is available, such as at the start of a wind turbine when you want to pump with a set pressure.

Referring to Figures 7A and 7B, it is shown how the interchangeable unit in an alternative embodiment comprises at least one cam curve and at least one eccentric. The design of the pump / motor has an integrated gear function. The design of the pump / motor includes at least one high gear and at least one low gear.

In the exemplary embodiment, the interchangeable unit 10 comprises at least one axis! 4 with associated eccentric 17. The eccentric 17 in turn affects a substantially annular part 19 which comprises at least one cam curve. The inner diameter of the annular part 19 may vary within the scope of the inventive concept. In the exemplary embodiment, the annular portion 19 comprises at least a first cam curve and at least a second cam curve. In alternative embodiments, the annular portion 19 may include multiple cam curves. The construction comprises at least one device 36, function, with which the eccentric 17 and the annular part 19 can be loaded and disengaged, respectively, and boarded. In the exemplary, but not limiting embodiment, the device 36 consists of a welding device 36 which comprises at least a first welding means 37 and a second welding means 38 which can be welded and disengaged from each other, respectively.

When the annular part 19 and the eccentric 17 are loaded in relation to each other, as exemplified in Fig. 7A, the annular part 19 with the cam curve will rotate at the same speed as the shaft. The cam curve will often perform an eccentric motion. In this position, the pump / motor is particularly suitable for a relatively lower speed on the input or output shaft! (depending on whether the device is used as a pump or motor).

When the ring the annular part 19 is disengaged from the eccentric 17, as shown in Figure 7B, the annular part 19 will again only move to a limited extent (it does not rotate but performs a limited movement influenced by the eccentric). When the shaft rotates, the annular part is affected to move in the radial direction on a corresponding sail as the shape of the eccentric. In the disengaged layer, the pump / motor is particularly suitable for relatively higher speeds on the input or output shaft (depending on whether the device is used as a pump or motor).

In alternative embodiments, the motor / pump comprises at least one actuator or the like which is intended to be used to feed (indicate) where the piston is in relation to the cylinder. In alternative embodiments, the position of the piston can be fed with a different type of suitable technique. The legislator is used to feed the angle and speed on the output or input shaft.

In the detailed description of the present invention, construction details and sub-techniques may be omitted which will be apparent to one skilled in the art to which the subject matter relates. Such obvious design details to the extent required for a proper function are to be obtained for the present invention. For example, the required control system, or control system, is used to control the functions of the pump / motor.

Although certain preferred embodiments have been shown in more detail, variations and modifications of the method and apparatus may become apparent to those skilled in the art to which the present invention pertains. Thus, it is possible that embodiments are combined where possible. All such modifications and variations are considered to fall within the scope of the appended claims.

It is conceivable that the present invention may be defined as a method for controlling the surface pressure between at least one cam roller and at least one cam curve in accordance with Figure 6 with the accompanying description on page 8.

In alternative embodiments it is conceivable that one of the chambers of the cylinders is intended for pumping air (compressing air, or gas or gases) and the other of the chambers for pumping water or other liquid.

A pump that pumps air and a pump for water or liquid. When you pump air, you get a lot of heat, which can be transported away with the water. A hybrid pump that sucks a little water on the low pressure side to a large air-water mixture flow on the pressure side.

Advantages of the present invention The present invention provides a number of advantages. The most obvious is that a hydraulic motor / hydraulic pump is obtained with which at least one of the previously mentioned problems has been eliminated or reduced. 11

Claims (11)

Patent claims A pump / motor (1) comprising a housing (2) comprising at least three cylinder / piston units (3), each comprising at least one cylinder and at least one piston, which are driven by pressurized medium or pressurized medium and the pump / motor comprises at least one unit (10) for converting rotary motion to forward and reciprocating motion of the pistons in the cylinders or alternatively converting forward and reciprocating motion of the pistons in the cylinders to a rotating motion can be characterized by the unit (10) for converting rotary motion to reciprocating of the pistons in the cylinders, alternatively converting forward and resurgent motion of the pistons in the cylinders to a rotating motion, is interchangeable, whereby it is possible to adapt the pump / motor to speed. Pump / motor (1) according to claim 1, characterized by the rotated movement in the third embodiment of the unit (10) is transmitted to or from the pistons via at least one eccentric (17). Pump / motor (1) according to claim 1, characterized by the rotary movement is transmitted to or from the pistons via at least one first cam curve and at least a second cam curve. Pump / motor (1) according to claim 1, characterized by the rotary movement in the first embodiment of the unit is transmitted to or from the pistons via at least one eccentric (17) and via at least one cam curve. Pump / motor (1) according to at least one of the preceding claims 3 or 4, characterized in that the pump / motor comprises at least one first cam curve and at least one second cam curve which control the movement of the pistons in one radial direction and the pump / motor comprises at least one third cam curve which steers the piston in the opposite radial direction. Pump / motor (1) according to at least one of the preceding claims 4 or the carriage of the motor comprises at least one first cam curve and at least one second cam curve which control the movement of the pistons in one radial direction and the plunger / motor comprises at least a third cam curve and at least a fourth cam curve which guides the piston in the opposite radial direction. Pump / motor (1) according to claim 1, characterized in that each cylinder / piston unit (3) comprises at least one cylinder unit (4) and at least one piston (5), the piston (5) of which is connected to, or integrated with , a piston rod (8), the piston rod (8) of which comprises at least one thrst part (16) which is rotatably connected via at least one axis of rotation (19) to at least one disc-shaped part (15), saint aft the position of the piston rods (8) in radial direction influenced by an eccentric (9), via the disc-shaped part (15), and the cylinder / piston units (3) comprise double-acting cylinders comprising at least one first chamber (6) and at least one second chamber (7). Pump / motor (1) according to one of the preceding claims, characterized in that the construction comprises at least one device, system or subsystem, for controlling the surface pressure between at least one cam roller and at least one cam curve. Pump / motor (1) according to one of the preceding claims, characterized in that the first chamber (30), A-chamber, and second chamber of the cylinder units, B-chamber (31), are connected to each other via at least one duct whose duct is provided with at least one valve (35) which opens or closes the channel between the first chamber (30) and the second chamber (31). Pump / motor (1) according to one of the preceding claims, characterized in that the first chamber (30), A-chamber, and second chamber of the cylinder units, B-chamber (31), are connected to each other via at least one duct whose duct is provided with at least one valve (35) which opens or closes the channel between the first chamber (39) and the second chamber (31) and all the construction comprises at least one valve (33) which controls & Wet into the first chamber (30) and at least one second valve (34) which controls the flow to the second chamber (31). --- k`-. M 0: N ir- (6, t7 1 1: 111'1 # 0114444 1416104: 01114 till t, l 02 'IL) \ -. LC) L (, „Vi $ 11141414141 11 • 1 • 141: 11111011 2 2 / Z .: 0: e 11. 11 ,, ■: ,,, v, 0. 6 1. 1 •• oo. •• 00 4103 00 0. 1 * * tfis le. 00 oO • -1159) -j / ..xxSXMXN% X \ NX- ■ II la 0 II`% Ir470 1 111; re r i 3Z. Z3 2_ Z litvoiliviofto ... iai _ Ar Apr% 4A V A re% ■ - • Lg-.11 iraliablet 7 / OQ,