KR20080011181A - Rotor sliding-vane machine - Google Patents

Abstract

A rotor sliding-vane machine comprises a rotor including working (1) and supporting parts (4) connected via force chambers (6) of variable length so that they rotate synchronously with a possibility of little reciprocal axial movements and tilts. The vanes (8) are located in vane chambers (7) of the working part (1) of the rotor and when the rotor is rotating they cyclically change the degree of protrusion into the annular groove (2) made on the face surface of the working part of the rotor. Between the supporting cover plate (5) of the housing and supporting part of the rotor there are supporting cavities hydraulically connected via the means of local pressures balancing to the force chambers of variable length and cavities of the working chamber in the annular groove of the working part of the rotor. Supporting cavities and force chambers of variable length are made so that pressure forces of the working fluid contained in the force chambers significantly balance pressure forces of the working fluid forcing out the working and supporting parts of the rotor from the working and supporting cover plates of the housing providing just a small tightening required for insulation.

Description

Rotor sliding vane device

TECHNICAL FIELD The present invention relates to device engineering, and can be used as a high pressure rotor sliding vane device that can operate in both a hydraulic motor and a pump mode with excellent efficiency and reliability and has a surgeless discharge function.

In order for the sliding vane pump to provide a fluctuating discharge function and high efficiency, it must have one constant cross-sectional area of the working chamber in the transfer zone, less loss due to leakage and friction, and no cavitation. This property should be maintained for all operating ranges of displacement alteration, pumping pressure and rotor rotational speed and should be hardly affected by working fluid contamination and wear of the pump elements.

For example, placing the working chamber at the face of the rotor, such as the pump of US Patent US570584, provides a constant cross-sectional area of the desired working chamber, and the pump displacement adjustment of US Patent US2581160, Russian Patent RU2123602, and US Patent US6547546. Combines well with

Placing the working chamber in an annular groove of the face of the rotor of the pumps of US Pat. Nos. 10,096,804, US3348494, US894391 and US2341710 provides a firm fixation of the vanes in the working chamber and the radial unloading of the rotor. The main sealings between the parts that reciprocally rotate in such a pump are the face surfaces of the corresponding rotor parts (hereinafter the working part of the rotor) in which the annular grooves are made, and the housing cover plate bonded to the annular grooves. It is transposed to the corresponding face surface of the following (operating cover plate of the housing). The sealing surfaces of the rotor and the housing can be made flat. Thus, moving one sealing surface closer to another sealing surface makes it easier to solve technical, thermal and other clearances between the flat sealing surfaces as the actuating parts of the rotor press the actuating cover plates of the housing.

In order to provide such a seal, the working fluid contained in the working chamber between the operating cover plate of the housing and the rotor face in the pumping and transfer zones may be deformed and separated from the operating part of the housing and the operating part of the rotor. Overcome the pressure

The use of mechanical compression means without hydrostatic balancing in the pump to create high pressure in the pressure line is not efficient due to large friction losses.

European patent EP0269474 describes a hydrostatic component characterized by less influence of axial rotor deformation on the seal quality and the use of working fluid pressure for reciprocal compression of the sealing surface of the rotor and housing. (This patent does not specify how to install it on the pump). The rotor of hydrostatic components consists of two parts, which the inventors call "vane holder" and "support flange". In a force chamber connected to the working chamber, a piston-like element that slides in the axial direction and engages the support flange is mounted on the face behind the vane holder opposite the face with the annular groove. Here, by moving the piston like element axially out of the force chamber of the vane holder, it is possible to solve the clearance between the vane holder and the housing which the inventors call a "guideway carrier". The working fluid pressure applied to the vane holder from the working chamber side is transmitted to the support flange through the force chamber and a piston like element. However, the hydrostatic component cannot retain hydrostatic balancing means from the opposite side of the support flange. The specification points out that, according to the heart of the present invention, the fluid pressure is compensated for by the flexible deformation of the flange so that the vane holder does not deform in the axial direction, but the rotor remains hydraulically unbalanced throughout.

According to the core of the invention described in the specification of European patent EP0269474, which unloads the friction sealing pair of the vane holder with the guide carrier and transmits the force in static contact with the deformable support flange of the piston like element. The contact seals the force chamber and the vane chamber connected to the force chamber. As the vanes move axially in the rotor, fluid moves through the vane's channels into the vane chamber. Increasing the rotor rotational speed and axial speed of the forward transfer vanes reduces the pressure in the vane channel. When the pump is operated in self-suction mode, for example, if the inlet pressure is equal to atmospheric pressure, cavitation occurs in the vane chamber at a certain rotor rotational speed (hereafter maximum self-suction speed). Cavitation not only increases noise and pulsations, but also significantly reduces the power and efficiency of the pump. Thus, this cavitation effect is considered a factor of dissipative loss that reduces the efficiency of the pump in the same context as the friction decreases in the face seal of the rotor and vane. If the possibility of cavitation is high and thus the maximum self-suction rate is lowered, the hydrostatic components may not function effectively.

European patent EP0265333 describes a hydrostatic differential gear embodiment in which a hydrostatic rotating thrust block is mounted between a support flange and a vane holder rear face that rotate at different speeds. The hydrostatic rotating thrust block is a thin, simple ring with a rigidly fixed rotation to the vane holder and a chamber opposite the support flange. Each of these chambers is hydraulically connected to the facing force chamber through a calibration orifice based on the hydrostatic bearing principle that the inventors call "oil thrust blocks." This pressure causes the force to be transferred to the support flange, which results in less deformation of the flange than similar deformation of the vane holder. The specification indicates that the deformation of the rotating thrust block is similar to the support flange deformation. That is, the rotating thrust block so that the pressure of the fluid applied to the rotating thrust block from the vane holder side exceeds the sum of the fluid pressure from the flange side and the elasticity of the rotating thrust block so that the rotating thrust block is deformed at an angle to be joined to the support flange. Will be transformed. Indeed, in the principle that the oil thrust block acts as a hydrostatic bearing, the pressure in the rotating thrust block chamber depends on the correlation between the reduction in the pressure force of the calibration orifice and the reduction in the pressure force of the clearance between the support flange and the rotating thrust block. Assume Thus, if the clearance is large and the pressure in the rotating thrust block chamber is significantly lower than the pressure in the force chamber, the rotating thrust block moves more closely to the support flange due to the corresponding pressure difference. The decrease in clearance increases the pressure in the rotating thrust block chamber, which coincides with the pressure in the force chamber through which the rotating thrust block chamber is connected through the calibration orifice. For example, if the rotating thrust block is fully engaged with the support flange, the oil thrust No leakage occurs in the block. In order to join as described above, the rotating thrust block must also be deformed according to the flange deformation, which requires that the rotating thrust block has a hydrostatic significant imbalance.

As mentioned for complete joining with the support flange, the flexural deformation of the rotating thrust block results in increased friction losses. When the flange deforms due to the pressure of the fluid and the thrust block joins the flange, the deformed flange and the undeformed thrust block are first partially alternated and the thrust block is deformed. In this case, if the block is not deformed due to the elasticity of the thrust block, the friction between the rotating thrust block and the support flange at the partial contact point is reduced accordingly. The thrust block is separated from the flange due to the pressure of the fluid that is constantly dispersed in the insulating clearance, and by the individually dispersed pressure, for example, the force chamber is reduced to zero in the interval between the force chambers. The flange is pressed from the side. As such, when using the pressing method from the force chamber side, the rotating thrust block must be so strong to obtain the desired insulating effect. In other words, the higher the pressure, the greater the friction loss corresponding to the elasticity of the deformed thrust block.

To reduce leakage with micrometer level clearance or no clearance at all, the hydraulic resistance of the calibration orifice and the resistance of the fine corresponding clearance must be similar. The use of the rotor rear face to draw fluid into the vane chamber through the cavity of the hydrostatic thrust and the cavity of the housing is not allowed. Thus, the above-mentioned drawback of the device, that is, the problem of increasing the cavitation tendency, is also not solved.

In addition, the use of hydrostatic bearings with calibration orifices to reduce friction reduces the reliability of the device. First, when suspended particles enter the fluid, the fine calibration orifice is blocked, resulting in a significant increase in pressure and frictional losses in the thrust block and a significant increase in wear rate. Secondly, if there is a local defect on the sealing surface, leakage from the chamber of the rotating thrust block increases and the pressure in the rotating thrust block chamber decreases. In this case, even if you press harder due to the increased pressure force difference, the leakage is not reduced and the balance is maintained, but the friction loss increases and the sealing surface wears quickly. Such additional leakage from the oil thrust block chamber results in a small change in volumetric efficiency but a significant increase in friction losses.

For the hydrostatic balance of the hydrostatic differential gear rotors described in European patents EP0269474 and EP0265333, the corresponding specification assumes two embodiments using a pair of hydrostatic components of this type.

In the first embodiment, two guideway carriers are mounted on both sides of one central vane holder. The force chamber is made at the rear of the guideway carrier which performs the function of a sliding seal fixed to the housing. In this case, one complete rotor with two working chambers is formed in two annular grooves on both faces of the rotor similar to that described in US Pat.

In a second embodiment, two vane holders are mounted on either side of one central guideway carrier. The vane holders carry a support flange which is rigidly joined to each other using a hollow cylindrical body forming a uniform and rigid element via the force chamber, referred to as the "sealed crankcase" in the specification of European patent EP0265333.

In two embodiments of the dual device, a unit formed from two guideway carriers is referred to as a stator unit or housing. This is because the position of the corresponding suction and pumping port does not change during rotor rotation. The first embodiment of the dual symmetric device is called a device with an inner rotor or housing force closure, and the second embodiment is called a device with an inner stator or rotor force closure.

In both of the above embodiments, the pressure force of the working fluid applied between the rotor and the housing in the pumping area of one working chamber is balanced in the second working chamber by the reflective symmetrical force. In this case, both working chambers must have a reflection symmetry with a plane perpendicular to the rotor axis of rotation.

In the transfer zone, the axial balancing of the fluid pressure force applied to the rotor is not only dependent on the working chamber balance but requires special care.

In the forward transfer zone during rotor rotation, sliding insulation contact between the vane forward transfer limiter, the vane's vane chamber, the contact of the rotor's insulating surface and the corresponding surface of the housing, and the rotor, vanes and A closed and transferred volume, separated from the suction and pumping area, by different clearances between the housings appears and moves. The local pressure at each of the transferred volumes of the others being partitioned depends on the difference in leakage into and out of this transferred volume, and then of all sliding contacts that insulate the transferred volume for different rotation angles upon rotation. It depends on the character of abutment of the surface. Here and subsequent sliding insulating contact surface adjacency refers to the hydraulic resistance of the clearance and its form between such surfaces as a function of two parameters: the angle of rotation of the rotor and the angle of the contact point relative to the housing selected point. do. The individual bonding characteristics of each surface pair of each device are due to technical inaccuracies in the manufacturing process and local defects that appear on the surface due to wear and thus distribute the insulating clearance resistance for different rotation angles of the rotor in different housing zones. Occurs. By distributing the clearance resistance, it is possible to greatly disperse local pressures occurring at different transferred volumes. Similar explanation applies to the backward transfer zone.

Since the dual symmetric device with the internal stator described above has no means of balancing local pressure in the transfer zone, the transferred volumes in the transfer zones of both symmetrical operating chambers are not connected to each other. In the case of a double symmetrical device with an internal rotor (US Pat. No. US3348494) there is a channel connecting the symmetrical vane chamber to the rotor. However, the symmetric cavities formed in both annular grooves of the transfer zone between the vanes are not connected to each other. Therefore, due to the individual bonding characteristics of the insulating contacts, each working chamber has a different local pressure per transfer zone and no rotor balancing. The friction in the face seal is reduced accordingly because the pressure forces applied to the rotors in the two symmetric chambers can vary variably as described above. For example, if wear causes local defects on the sealing surface of the vane, rotor or housing, the hydraulic resistance affecting the local pressure in the transferred volume is greatly dispersed. Even if the total leakage with less effect on volumetric efficiency is slightly changed, the pressure force varies significantly, the friction on the side with less local pressure increases (e.g., the area with greater wear area), The wear rate is also fast.

In the pump of US Patent US3348494, the vane of the rotor is caused by a special vane drive mechanism rather than a spring. It consists of a single cam slot mounted to the housing, which passes along the vane's side lobe through the special driving window of the rotor slide. Those skilled in the art will appreciate that such vane drive mechanisms must be hydrostatically insulated with the working chamber.

In such embodiments implementing vane drive mechanisms outside the actuating chamber, vane friction losses to the housing surface are reduced, but the walls of the vane chamber provide hydraulic insulation of the vane drive mechanism to bond the vane's sliding insulating contact surfaces. The dependence of local pressure on properties is increased. If the joining characteristics change due to wear, leakage between the working chamber cavity and the cavity in which the drive mechanism is installed increases and local pressure is dispersed.

In two embodiments of the dual symmetry device, the vanes moving axially in the vane chamber are replaced with fluid entering through the channels of the vanes themselves. Thus, such designs continue to have significant weaknesses due to cavitation losses.

Russian patent RU2215903 describes an embodiment of a pump that provides hydraulic rotor balancing means and is not affected by cavitation of the vane chamber. This patent describes a reversible rotor device comprising two annular grooves that form the working chamber at both faces of the rotor. Both annular grooves pass through the vane's through hole. Each cover plate of the housing has a forward transfer limiter and a backward transfer limiter that are axially movable. The inventors call these limiters "adjustment elements" and "partitions", respectively. A feature of the reversible device is that the two working chambers are asymmetrical to each other. That is, there is one adjustment element of the second operation chamber mounted opposite the partition of the first operating chamber and one partition of the second operation chamber mounted opposite the adjustment element of the first operating chamber. Here the “operating cavities”, which the inventors understand as suction and pumping cavities in both chambers axially opposite each other, are connected to the channels. Thus, the suction cavity of the first working chamber is connected to the pumping cavity of the second working chamber on the opposite side, and the pumping cavity of the first working chamber is correspondingly connected to the suction cavity of the second working chamber.

As the vanes move from the rotor to the suction cavity of the working chamber, the fluid from the opposing pumping cavity of the remaining working chamber fills the empty volume of the vane chamber through the vane chamber of large cross-sectional area. Thus, the cavitation tendency of the vane chambers is not a feature of such a design.

When such a device is activated, the pressure increases in one of the connected operating cavity pairs and the pressure decreases by that in the second pair. The possibility of balancing the hydrostatic rotor in the region of the suction and pumping cavities in such a device is evident.

In the transfer zone, due to the antisymmetry of the working chamber, the configuration of the transferred volume for the opposite rotor faces is different and the insulating means are also different. Between the rotor and the adjustment element, a transferred volume insulated by the face of the vane sliding along the adjustment element is formed in a confined groove. Between the rotor and the partition opposite the adjustment element, a transferred volume insulated by the bottom section of the annular groove sliding along the partition is formed in isolation from the vane chamber. The distribution of transferred volume pressure and pressure in the clearance of the sliding insulating contacts is such that the shape and size of the clearance, for example the sliding insulation with one partition of the annular groove bottom sections and with one adjustment element of the vane It depends on the bonding properties of the surface of the rating contact. Different pressure distributions on the opposite faces of the rotor produce variable different forces in the rotor of each transfer zone, even if the contacts are ideally flat.

For example, as a result of wear, local deflection from scratches, scratches and other local defects appear on the sealing surfaces of the adjustment elements, partitions, annular groove bottoms and vane faces of the sliding insulating contacts. Properties, thereby changing the correlation between the pressure dispersion and the local pressure. In addition, even if the total leakage does not change very much, the variable differential pressure increases markedly, friction increases, and wear speed is increased.

For example, a method of providing face sealing between the rotor and the cover plate of the housing for both rotor faces by a precise manufacturing method such as US Pat. No. 3,394,944 is not suitable, which is generally due to thermal expansion, deformation and wear. This is because the clearance change due to exceeds the allowable clearance for the seal operating at high pressures. Thus, the rotor device structure also includes an axially movable sealing element, for example a guideway carrier with a force chamber opposite the guideway described in European patent EP0269474. If the corresponding elements are not balanced, frictional losses occur accordingly. Such movable sealing is described in detail below.

As a solution to overcome the tendency of cavitation to occur in the vane chamber of the pump, means for reducing the influence of the bonding characteristics of the sliding insulating contacts of the working chamber on maintaining the rotor balance, and moving in the axial direction as described in Russian patent RU2175731 Possible sealing elements are considered by us to be the most similar.

The patent describes one pump having one housing comprising an actuating and support cover plate referred to as a “housing cover plate”. On the rotor face opposite the working cover plate of the housing there is a cylindrical annular groove passing through a vane called "displayer" in the patent and a vane chamber called "opening of the rotor" in the patent. The surface of the rotor face with a cylindrical annular groove can be in sliding contact with the face of the sealing element on the opposite side and mounted in a slot of the operating cover plate of the housing. The pump includes one backward transfer limiter, referred to in the patent as a “partition” that separates the pumping cavity and the suction cavity. The suction cavity is connected with an inlet port, referred to as "inlet opening" in the patent, and the pumping cavity is connected with an outlet port, referred to as "outlet opening" in the patent. The surface of the backward transfer limiter is in sliding contact with the rotor means for backward transfer insulation, referred to in the patent as the “inner surface of the cylindrical annular groove”. The backward transfer limiter may be secured to the operating cover plate of the housing to form a complete single unit therewith, but in some pump embodiments the backward transfer limiter may be mounted so as to be able to move in the axial direction, and the means for pressing against the rotor Can interact with The pump includes a vane drive mechanism, referred to in the patent as "mechanism for setting the axial arrangement of the displacer with respect to each other". The forward transfer limiter is formed as part of the inner surface of the working cover plate. For adjustable device embodiments, the patent refers to the forward transfer limiter as an “insulating element movable in the axial direction”. The second face of the rotor is in contact with the support cover plate of the housing. The support cover plate of the pump housing offers the possibility of mounting a support-distributing member, referred to in the corresponding invention as a "supporting-distributing disc". The support-distributing member can be mounted to move along the rotor axis. The support-distribution member also performs a dispensing function and includes a support cavity, referred to in the corresponding patent as a "support-distribution cavity". The support-distribution cavities are located facing the transfer area providing sliding of these support cavities in sliding contact with adjacent back face surfaces from the suction and pumping cavities of the working chamber and their insulation (insulating partition). . Each support-distribution cavity is connected to the opposite suction or pumping area, respectively, through a channel made in a rotor or housing containing vanes. The dimensions and shape of the support-distribution cavity are similar to the dimensions and shape of the pumping and suction cavities of the working chamber. The vane chamber of the rotor is made of a through channel leading to the support-distribution cavity in the suction and pumping area.

The through channels of the vane or of the rotor simultaneously connected to the suction cavity of the working chamber are in this case connected next to each other and via the support-distribution cavity to the channels of the housing. This significantly reduces the cavitation tendency of the pump and greatly increases the maximum self-suction rate.

The use of the support-distribution member also contributes significantly to the hydrostatic balancing of the rotor, so that the possibility of balancing the pumping and suction areas becomes apparent.

In the transfer zone, the insulator clearance of the working chamber against the difference in counter pressure forces exerted on the two faces of the rotor because the rotor or vane has the through channel so that the pressure at the two faces of the rotor is similarly distributed. It is possible to reduce the influence of spread and connected local pressure. However, the configuration of the rotor face is different so that the rotor is not perfectly balanced. Incomplete balancing of the rotor causes the pressure applied to both faces of the rotor to vary variably and also to reduce friction against the face seal.

The pressure distribution behind the rotor of the transfer zone depends on the bonding characteristics of the sliding insulating contact between the rotor and the insulating dams of the support-distributing member. Thus, for example, the similarity of the pressure distribution is also greatly hindered if the joining characteristics change due to the occurrence of scratches on the sealing surface due to wear or the occurrence of deflection from a flat shape. In addition, even if the total leakage does not change very much, it brings about a marked increase in the variable difference in pressure force, the friction is increased, and the wear rate is faster. The following is a description of the other components that lead to frictional losses on the face seal.

On the inner surface of the support cover plate of the housing there is one slot in which at least one sealing element is mounted so as to be able to move along the rotor rotational axis. The inventors point out that support-distribution members, referred to as support-distribution discs, can be used as such elements. In the slot on the inner surface of the operating cover plate of the housing are mounted two sealing elements which can move along the rotor rotation axis.

The sealing element is made of a hollow cylinder located in an annular slot on the inner surface of the housing cover plate and can move along the rotor axis of rotation. In order to press the rotor surface as needed with a movable sealing element, the element is supported by a special force chamber made inside the housing in which increased pressure is formed. In the device, the role of such force chamber is played by the annular slot. The hollow cylinder has a through channel connecting the annular force chamber to the leak zone of the face sealing clearance in order to increase the pressure of the annular force chamber. The value of the increased pressure of the annular force chamber is determined by the shape, dimensions and position of the channel.

The movable sealing element mounted in the housing of one cylindrical slot with the same total pressure of the pressure causes a large frictional loss due to the strong press of the rotor in the transfer zone and in part in the suction zone.

European patent EP0269474 points out the possibility that several force chambers in the housing can be insulated from one another. Different pressures are generated in these chambers so that the movable sealing element represented by the guideway carriers supported by these chambers can be properly hydrodynamically balanced in the pumping and suction region. Also for two reasons, in the forward and backward transfer zones, the movable sealing element is subjected to variable forces from the rotor side. The first reason is that the area of the transfer zone at the edge of the transfer zone connected to the pumping or suction zone changes periodically. The second reason is that the pressure of the working fluid volume delivered in the forward or backward transfer process between the suction area and the pumping area is constantly changing and the position with respect to the housing is also constantly changing. As a result, in the transfer zone a complex and constantly varying pressure distribution is formed which is applied to the movable sealing element from the rotor side. In order to create a continuously varying symmetrical pressure distribution between the movable sealing element and the housing, it is necessary to place many force chambers insulated from each other and very small and infinitely, each force chamber connected to the corresponding point of the transfer zone and bonded It is insulated with one force chamber. The actual number of possible force chambers in the housing of the transfer zone is very small, and the variable force applied to the movable sealing element is not fully compensated. Thus, the surface of the sliding insulating contact of the rotor presses the housing sealing element with variable force.

For example, local defects in the sealing surface, such as abrasion, resulting in a change in the joining characteristics by the rotor of the sliding insulating contact of the movable sealing element greatly expands the hydraulic resistance that determines the local pressure of the transferred volume. In addition, even when the total leakage does not change very much, the pressure is significantly increased, the friction is increased, and the wear rate is also increased.

The size of this variable component, which achieves a large value, determines the inherent friction loss level of the above mentioned pump, which is fixed to the housing with a movable seal.

Therefore, not all solutions for maintaining the hydrodynamic balancing of the rotor and the movable seal considered above contribute to the complete balancing of the rotor and the movable sealing. For example, if wear causes local defects in the sealing surface and the joining properties of the sliding insulating contacts are not ideal, then large pressures occur in friction pairs between the rotor and the sealing elements of the housing. The need to prepare for such large pressures requires that the sliding insulating contacts of the sealing shoulders of the face seals are relatively wide, resulting in an increased effect of local defects on the sealing surface on pressure force imbalance.

A feature of all the structures described above is the reduced efficiency due to the increased dissipation losses. The above-mentioned means of reducing friction due to hydrostatic balancing of the rotor and movable sealing cannot achieve a perfect balancing effect, and cope with changes in the bonding properties of the sealing surface of the sliding insulating contacts due to local defects and contamination of the working fluid. can not do. Even insignificant leakage changes in terms of impact on volumetric efficiency can significantly reduce mechanical and overall efficiency.

It is an object of the present invention to create hydrostatic balancing of a rotor and a removable seal that is resistant to wear of the device elements and working fluid contamination and compatible with the means of overcoming cavitation of the vane chamber, To improve the efficiency and reliability of vane rotor devices.

To solve the specified problem, the rotor is made adaptive. That is, it consists of a working part and a supporting part which perform a function of a moving seal. There are vane chambers in the actuating part of the rotor, and an annular groove is made in the actuating face surface of the actuating part, which is the vane chambers with vanes kinematically connected to the vane drive mechanism mounted in the housing. Is connected to. The housing, which has an inlet and an outlet port and comprises an operation cover plate and a support cover plate having one forward transfer limiter and one backward transfer limiter, is connected to an alternately rotatable rotor. The operating cover plate of the housing is in sliding insulating contact with the operating face surface of the operating part of the rotor, and forms an operating chamber in the annular groove, the former being in sliding insulating contact with the backward transfer insulating means of the rotor. The transfer limiter and the forward transfer limiter in sliding contact with the vanes into the suction cavity of the working chamber hydraulically connected to the inlet port and into the pumping cavity of the working chamber hydraulically connected to the outlet port. A vane transfer mechanism and a vane drive mechanism are made to allow vanes to separate at least one vane internal cavity of the working chamber by the pumping and suction cavity rudder vanes.

The support cover plate of the housing is in sliding insulating contact with the support surface of the support part of the rotor opposite the operating surface of the operating part of the rotor. The support part of the rotor is kinematically connected to the actuating part of the rotor by an assembly of rotor elements comprising a force chamber of variable length such that both of these parts of the rotor are corresponding cover plates and sliding insulators of the housing. The support part and the actuating part of the rotor rotate at the same time so as to be able to axially move or tilt at least enough to allow a rating contact. There are support cavities with insulating means made between the support cover plate of the housing and the support part of the rotor. Each of the formed vane inner cavities, the pumping cavity and the suction cavity, are hydraulically connected to at least one force chamber and at least one support cavity of variable length via local pressure force balancing means. The shape, dimensions, and position of the support cavities and the insulation means are generally the same in working fluid pressure forces that repel the actuating part of the rotor from the actuating cover plate of the housing, pushing the support part of the rotor out of the support cover plate of the housing. It is selected to be in the opposite direction to the pressure forces of the working fluid. The variable length force chamber is comprised of the pressure forces of the working fluid in which the pressure of the working fluid contained in the variable length port chamber, regardless of the rotor rotational angle, pushes the parts of the rotor out of the corresponding cover plate of the housing. It is designed to balance and provide only the small pressure needed for insulation.

The core of the present invention will be described by the following drawings, in the drawings,

FIG. 1A is a partially nodal cross-sectional view of the rotor as seen from the working part side of the rotor, showing a rotor sliding vane device with one adaptive rotor and a housing force closure, with the operating cover plate, vane drive mechanism and housing linking element of the housing not shown; No;

FIG. 1B is a partially nodal cross-sectional view of the rotor seen from the working part side of the rotor, showing a rotor sliding vane device with one adaptive rotor and a force closure to the housing, the support cover plate of the housing, the vane drive mechanism And the housing linking element is not shown;

2a shows a forward and backward transfer limiter of a rotor sliding vane device with a force closure of a housing (housing in the form of a hollow cylinder) with cover plates linked by a linking element external to the rotor and one adaptive rotor; An axial sectional view of a plane passing through them;

2B passes through inlet and outlet ports of a rotor sliding vane device with a force closure of a housing (housing in the form of a hollow cylinder) with one adaptive rotor and cover plates linked to one linking element external to the rotor; Axial sectional view of a plane;

FIG. 2C shows the inlet and outlet ports of a rotor sliding vane device with a force closure of a housing (“bobbin” shaped housing) with one adaptive rotor and a cover plate linked to one linking element within the rotor; Axial cross section of the plane passing through;

FIG. 2D shows the inlet and outlet ports of a rotor sliding vane device with one adaptive rotor, a rotor force closure to the rotor, and a support part of the rotor combined with a rotor linking element made in the form of a “bobbin” Axial sectional view of a plane through the field;

FIG. 2E has a working part of the rotor combined with one adaptive rotor, a rotor force closure and a rotor linking element made in the form of a “bobbin”, with two working chambers on both parts of the rotor and two sets of vanes An axial sectional view of a plane through a forward and backward transfer limiter of a rotor sliding vane device having a;

2F shows an axial cross-sectional view of a plane through a forward and backward transfer limiter of a rotor sliding vane device with one adaptive rotor, rotor force closure, and one rotor linking element made in the form of a “bobbin”. ) And axial cross-sectional view (b) through the inlet and outlet ports;

FIG. 2G shows a forward and backward transfer limiter of a rotor sliding vane device having vanes pivoted and having an actuating part of the rotor coupled with one adaptive rotor, a rotor force closure, and a rotor linking element made in the form of a “bobbin”. An axial sectional view of the plane passing through the shaft and an axial sectional view of the plane perpendicular to the rotor rotation axis and passing through the annular groove;

2H is an axial cross-sectional view of a plane through the inlet and outlet ports of a rotor sliding vane device having one adaptive rotor, a rotor force closure, and an actuating part of the rotor coupled with a rotor linking element made in the form of a hollow cylinder;

FIG. 2i shows a rotor with one adaptive rotor, a rotor force closure without a rotor linking element, and a rotor's actuation and support parts connected by a variable force chamber that operates to attract two parts of the rotor to each other; FIG. An axial sectional view of the plane through the inlet and outlet ports of the sliding vane device;

2J is a view of a rotor sliding vane device in which the vanes move radially, with one adaptive rotor, a housing force closure, and a variable length force chamber directly connected to the annular groove and the support cavity;

3A is a cross-sectional view of an embodiment of a variable length force chamber with one embedded element in the form of a piston having one force cavity and a spherical face;

FIG. 3B is a cylindrical containing element with one force ledge and a through channel and a spherical face supported by a support part of the rotor comprising a support cavity and a through channel. FIG. A cross-sectional view of an embodiment of a variable force chamber having a length;

3C is a cross-sectional view of an embodiment of a variable length force chamber having two force cavities and one cannular connector;

3D is a cross-sectional view of an embodiment of a variable length force chamber having two force ledges and one cannulated connector;

3E is a cross-sectional view of an embodiment of a variable length force chamber having a container element of the support part of the rotor, a force regime of the actuating part of the rotor, and one connector configured including the container element and the embedded element. ;

3F is a cross-sectional view of an embodiment of a variable force chamber that operates to attract two parts of the rotor to each other;

3G shows that one container element is made in the actuating part of the rotor, and a second container element comprising the support cavity and the through channel slides flat along the support part of the rotor and has a spherical face and one through channel. Cross-sectional view of an embodiment of a variable length force chamber, in which one connector in the form of a cylinder is supported by a second container element;

4A is a partial cross-sectional view of a circular development of the annular groove of the forward transfer zone;

4B is a partial cross-sectional view of the circular development of the annular groove of the backward transfer zone;

5A is a cross-sectional view of an embodiment of a local pressure force balancing maintenance means consisting of an annular groove, a channel of the actuating part of the rotor, a vane chamber, a channel of the force chamber, a channel of the support part of the rotor, a support cavity;

5b is a cross-sectional view of an embodiment of a local pressure force balancing maintenance means consisting of an annular groove, a channel of vanes, a vane chamber, a channel of a force chamber, a channel of a support part of the rotor, a support cavity;

5C is a cross-sectional view of an embodiment of a local pressure force balancing maintenance means consisting of a force chamber, a vane chamber, a channel of vanes, an annular groove, a channel of a housing operating unit, and a support cavity of the housing operating unit;

5D shows the implementation of a local pressure force balancing maintenance means consisting of a vane chamber, a vane channel, an annular groove, a channel of the housing operating unit, a support cavity of the support part of the rotor, a channel of the support part of the rotor, and a force chamber of variable length. Example cross section;

FIG. 5E is a partial cross-sectional view of the local pressure force balancing means, consisting of a support cavity in the form of a radial slot of a housing connected to a channel in the form of a longitudinal arc slot of a support part of the rotor; FIG.

5F is a cross-sectional view of an embodiment of a local pressure force balancing maintenance means, consisting of a force chamber of varying length, an annular groove, a channel of the housing operating unit, a support cavity of the housing operating unit;

6 is a cross-sectional view of an embodiment of a vane hydraulic tightening device of a vane chamber connected to both vane inner cavities joined through a valved channel;

7 is a circular annular groove, an embodiment of bottom unloading cavities and bottom sealing ledge, having a bottom cavity separated by two bottom ledges and adjacent two vane chambers and connected through a channel to a variable force chamber. Partial cross-sectional view of the deployment portion;

8A is a partial cross-sectional view of a circular development of an annular groove of an embodiment of a support cavity in which the support cavity of the rotor is connected to a channel of the rotor;

8B is a partial cross-sectional view of the circular development of the annular groove of the embodiment of the support cavity in which the support cavity of the rotor is connected to the channel of the housing;

9 is a partial cross-sectional view of a circular deployment of an annular groove of a rotor sliding vane device with a housing force closure and one adaptive rotor with a transferred volume of suction, forward transfer, pumping and backward transfer zones;

10 is a cross-sectional view of the cover plate of the housing comprising a strain relief chamber made between the functional element of the cover plate and the load bearing element.

The basic idea of the present invention is a rotor sliding vane suitable for use as a pump or hydro motor which can change or fix the rotor rotation direction and as a pumping-motor unit of hydromechanical transmission. It is to provide various embodiments of the device. In some embodiments, the housing is secured to a rack of aggregates and the rotor rotates relative to the housing and the aggregate rack. In another embodiment, the rotor can be secured to the aggregate rack and the housing rotates relative to the rotor. For example, when the rotor device is a hydraulic mechanical transmission mounting unit, an embodiment in which the rotor and the housing rotate relative to the rack of the aggregate is also possible. In the following, it is considered that the correlated rotation of the rotor and the housing is independent of the type of installation of the rotor apparatus of the assembly. In all cases, the rotor has a single annular groove in the face element and a unit with vanes that change the sliding angle to the annular groove by making cyclical movement with respect to the rotor each time the rotor rotates. it means. The housing is a unit in which the positions of the inlet and outlet ports do not change upon alternating rotation of the rotor and the housing.

The following describes a preferred embodiment of all the essential elements of the rotor device. In addition, the structure and operation of the preferred embodiment of the apparatus for performing the multipurpose pump function will be described in detail.

One adaptive rotor depicted in FIGS. 1A, 1B is provided with a face annular groove 2 made in the working face forming the working chamber and in sliding contact with the insulating surface of the working cover plate 3 of the housing of FIGS. 2A, 2B. The branches are divided into a working part 1 of the rotor and a supporting part 4 having a support face in sliding contact with the insulating surface of the supporting cover plate 5 of the housing. These two rotor parts can be connected to one another by the assembly of the rotor elements and rotate at the same time, but they can be moved slightly in the axial direction or tilted with respect to each other to maintain sliding insulation contact with the two cover plates of the housing during rotor rotation. have. The rotor element assembly comprises, for example, rotation synchronization means already known in the art, made in the form of a joint of the same angular velocities, and a variable-length rotor force chamber (6 in FIGS. 3a, 3b, 3c, 3d, 3e, 3f). Included, the pressure force applied to the rotor operating chamber 1 from the working chamber side and the force chamber 6 side of the annular groove 2 changes simultaneously in the transfer zone. Thus, the number of such force chambers 6 can be equal to or divided into the number of vane chambers 7, with each force chamber 6 of variable length being annular grooves 2 of the operating part 1 of the rotor. Hydraulically connected to), formed during rotation of the rotor in the annular groove (2) of the operating part (1) of the rotor of the forward transfer zone between the two joined vanes (8), and with the individual characteristics of the local pressure change Each cavity that is characterized is hydraulically connected to a force chamber 6 of variable length such that the local pressure of the cavity and the force chamber 6 connected to the cavity is approximately equal. In a preferred embodiment of the invention each force chamber of varying length is connected to the nearest cavity of the annular groove.

A variable length force chamber is made such that the actuation and support parts of the rotor required for insulation are moved alternately as the chamber length changes. According to the heart of the invention, the pressure force of the working fluid contained in the force chamber applied to the actuating and supporting parts of the rotor is not affected by the force chamber length change at a certain pressure.

The force chamber of varying length can be made different using, for example, bellows or flexible sidewalls. In a preferred embodiment of the present invention is formed of alternatingly mounted container elements and embedded elements, the outer wall of the embedded elements is in sliding contact with the inner wall of the container elements, the operation of the rotor required for insulation and It has one force chamber of variable length, which seals the force chamber when the support part alternates as described above.

Embedded elements and container elements can be made separate from the parts of the rotor but kinematically connected to each other. In a preferred embodiment of the invention, the containing elements or embedded elements are made directly on the rotor part. The first embodiment has one container element in the actuating or supporting part of the rotor which can be made of a force cavity such as a cylinder (14 in FIG. 3A), for example a device in which the rotor has a rotor force closure from below. The force cavities can be made in the linking element of the rotor when it comprises one linking element as described for. The second embodiment has an embedded element (10 in FIG. 3B) that can be made of a force ledge, such as a piston, in the actuating or supporting part of the rotor and in the linking element of the rotor.

If the alternating movement size of the actuating and supporting parts of the rotor is small, for example, a pair of container and embedded elements can be used to make the force chamber a hydraulic cylinder (FIGS. 3 a, 3b).

If the alternating movement of the rotor parts, in particular the magnitude of the alternating inclination, is as large as expected, the present invention can be applied to two container elements (11 in FIG. 3c) mounted such that, for example, a variable length force chamber can be alternated. And when the outer walls are formed by one embedded element in the form of a connector 12 in sliding insulating contact with the inner wall of the two container elements, a variable length force chamber is realized as two pairs of container and embedded elements. An embodiment is provided.

In FIG. 3g, one container element is made of a cylindrical cavity of the actuating part 1 of the rotor, and is fitted with a second container element 11 having an inner spherical insulating surface and an outer insulating plane, A flat surface is in sliding contact with the plane of the support part 4 of the rotor. In the embedded element in the form of connector 12 there are outer cylindrical and spherical insulating surfaces in sliding insulating contact with the inner cylindrical and spherical surfaces of the containing element.

In another embodiment, one container in the form of a connector 12 is provided by two embedded elements (10 in FIG. 3D) mounted in such a way that the force chamber is alternately movable and the inner walls are in sliding insulating contact with the outer walls of the two embedded elements. A first embedded element formed by an inning element or mounted such that the force chamber is mounted such that the force chamber is alternating with the first container element (11 in FIG. 3E), the outer walls are in sliding insulating contact with the inner walls of the first container element; The inner walls are formed by a second container element coupled with the first embedded element in one connector 12 in sliding insulating contact with the outer walls of the second embedded element.

The sealing of the sliding contact when moving or tilting in the axial direction is, for example, using a spherical sealing shoulder (13 in FIGS. 3a, 3b, 3c, 3d, 3e) at the outer surface of the embedded elements. Can be made according to.

Preferred embodiments of the present invention provide force chambers of varying length such that the container and embedded elements of the force chamber alternately substantially parallel to the rotor rotation axis when the force chamber length is changed. The pressure force of the working fluid contained in the force chamber is such that, for example, the embedded element is relocated from the containing element or pushed apart the pair of the elements by sliding contact to the connector. Embodiments of such force chambers are provided, which tend to increase the total spacing between the ends of the elements or tend to move the support and actuation parts of the rotor closer to the corresponding cover plates of the housing. In the case of a device embodiment with a rotor force closure described below, the invention also provides that the pressure force of the working fluid contained in the force chamber is such that, for example, the embedded element 10 is inserted into the containing element (11 in FIG. 3F). The ends of the elements by pushing to move the actuating and supporting parts of the rotor closer to each other and closer to the corresponding cover plates of the housing coupled to the actuating unit of the housing between the actuating and supporting parts of the rotor. Also provided is an embodiment of a force chamber of variable length, which tends to reduce the total spacing of the liver.

If desired, the force chamber can be made such that the alternating movement of the elements forming these chambers is not substantially parallel to the rotor axis of rotation. In this case, the assembly of rotor elements providing the kinematic connection of the actuating and supporting parts of the rotor has a forces direction to transfer the movement of the force chamber elements relative to the actuating and supporting parts of the rotor. Means for converting. The means for converting the force direction may comprise levers, cams or other elements that are known in the art for similar purposes in the art.

1A, 1B, 3C are force connected to vane chamber 7 and comprising cannular connectors 12 having force cavities 14 and sealing shoulders 13 of the support and acting parts of the rotor. Show the chambers 6. The sealing shoulder 13 is here mounted with the end in the force cavity to seal the force chamber when the actuating and supporting parts of the rotor alternately move or tilt in the axial direction.

According to the invention, the variable length force chamber has a flexible element, for example a spring, for pressing and sealing the rotor parts against the cover plate of the housing when the pumping pressure is low or absent.

In general, the vane inner cavities of the working chamber formed in the transfer zone of the annular groove 2 may not be connected to the cavity formed in the vane 8 and in the transfer zone of the vane chamber 7. In this case, the pressures of these cavities will change differently and for perfect balancing each of the cavities must be juxtaposed with a corresponding force chamber 6 of varying length. Their number may be divided by the number of vane chambers. However, in order to provide self sealing of the face surfaces of the vanes 8 sliding along the forward transfer limiter 15 (FIG. 4A), the cavity in the vane chamber 7 is replaced with the vanes opposite the vanes and the sealing face. It is convenient to connect from the face side to that cavity of the annular groove 2 between the adjacent vanes which push the fluid into the pumping cavity. In contrast, in the case of hydraulic motors, the fluid pushes the vanes out. Thus, in general, the cavity of the vane chamber 7 is located between the vane and the bonded vanes with a higher pressure to hydrostatically tighten the vanes 8 to the surface of the forward transfer limiter 15. It must be connected to the corresponding cavity of the two cavities in the groove. In this case, a pressure greater than the sealing surface is applied to the opposite face of the vane and the vane 8 is pressed against the forward transfer limiter 15 at a pressure proportional to the pressure difference between the inlet and outlet. To prevent excessive friction losses between the vane 8 surface and the forward transfer limiter 15, the vane surface is hydraulically connected to the cavity in the vane chamber bonded to the opposite surface of the vane and vane sealing ledge 17. It will have a loading cavity 16. The shape and area of the vane unloading cavity and the vane sealing ledge should be governed by the ratio optimizing means between the rate of leakage of clearance of the sliding limiter contact surface of the transfer limiter and vane and the amount of friction loss of the vane face on the forward transfer limiter.

One of the preferred embodiments of the present invention comprises an axially movable vane comprising a through channel 18 connecting the cavity of the vane chamber to the vane unloading cavity 16 of the vane sliding surface on the forward transfer limiter. 8) and the vane unloading cavity 16 which is adapted to be connected to the vane inner cavity described above. Another embodiment of the present invention provides channels (19 in FIG. 5A) made in the actuating part of the rotor connecting the cavities of the vane chambers with the corresponding vane tab cavities of the annular groove 2.

For this cavity connection, the number of insulated and transferred volumes is equal to the number of vane chambers of the working part of the rotor. Thus, the number of force chambers may be the same.

For switchable devices or reversible devices that can change the working fluid flow direction without changing the rotor rotation direction for use as a pump or as a motor, when the operating mode is changed, the position of the high pressure cavities is forward transferred. It is changed for the vane chamber selected in the zone. In this case, in order to provide the above-mentioned hydraulic tightness of the vanes, valve elements 69 are provided in the channel connecting the vane chambers to the annular groove in a hydraulic manner as described above, so that the vane chamber is joined to the vane with higher pressure. It is connected to the corresponding cavity in the annular groove between the vanes (FIG. 6). In this embodiment, it is reasonable to make several variable length force chambers connected directly to the cavities in the annular grooves between the vanes through the channels, and to create other variable length force chambers connected to the vane chambers. Do. For this connection, it is reasonable to choose the number of force chambers of variable length to twice the number of vane chambers of the operating part of the rotor. In this case, vane sealing ledges 17 sliding to the forward transfer limiter 15 separate the vane unloading cavities 16 from the joined two vane interior cavities of the annular groove 2. An embodiment of the through channels of the vane is also provided, wherein the vane unloading cavities are bound by the walls of the channels.

The pressure of the force chamber, which is variable in length, is always equal to the pressure of the corresponding cavity of the annular groove. To maintain the balancing of the fluid pressure force applied to the operating part of the rotor from the operating cover plate side of the housing with the fluid pressure force from the force chamber side, based on the pressure force distribution configuration between the operating part of the rotor and the operating cover plate of the housing. The size, shape and location of the force chambers should be selected. The pressure force is formed in both the fluid in the working chamber cavity, the fluid flowing between the junction cavities of the other working chambers, and the fluid flowing out of the cavities of the working chamber through the face seal clearance.

The present invention provides two embodiments of rotor means for backward transfer insulation.

In a first embodiment of the backward transfer zone and the forward transfer zone, the insulation is provided by sliding contact with the corresponding transfer limiter surface of the spots of the face surfaces of the vanes. In this case, the configuration of the cavities and corresponding seals between the operating part of the rotor and the operating cover plate of the housing, which determines the geometrical distribution of the pressure force of the working fluid which pushes the operating part of the rotor out of the operating cover plate of the housing, results in two transfers. Similar in zones, allows for easy determination of the required properties of the force chambers. In this case, however, it is necessary to take into account that the position of the higher and closest vane internal cavity for the selected vane chamber will be different for the forward transfer zone and the backward transfer zone as described above for the forward transfer zone of the reversible or convertible devices. do. Thus, the embodiment of hydraulic connection of the vane chambers with the annular groove for the hydraulic tightness of the vane chambers and the embodiment of the force chambers are similar to the embodiments described above for such a device.

In a second design embodiment the insulation in the working chamber of the forward transfer zone (B in FIG. 4A) is provided by sliding contact of the surface of the forward transfer limiter 15 of the vane 8, and the backward transfer zone (D in FIG. 4B). Insulation of the actuation chamber is provided by a sliding contact with the surface of the backward transfer limiter 21 at a point on the bottom of the annular groove of the rotor face. In this case, the configurations of the cavities of the annular groove and the corresponding seals connected to the corresponding force chambers are generally not the same for the forward transfer zone and the backward transfer zone. As a result, the pressure forces of the fluid exerted on the actuating part of the rotor from the actuating cover plate side of the housing may differ in the same pressure and value of the transferred volume of the forward and backward transfer zones. In addition, the centers of these forces exerted on the actuating part of the rotor are changed when applied to the same piece of rotor. The change in the fluid pressure force center applied to the actuating part of the rotor depends on the dimensions and position of the sealing surface of the vane face and the point of the annular groove bottom relative to each other.

In order to maintain the balancing of the influence on the working part of the rotor from the working chamber side of both zones in a constant force chamber configuration, the area of the sealing point of the groove bottom surface of the rotor is minimized and the sealing point of the vane face surface of these parts A method is provided to maximize the access to to minimize the change in geometrical characteristics of the annular groove cavities. For this purpose, the surface of the annular groove bottom between the vanes has bottom unloading cavities 22 and sealing ledges (23 in FIG. 4B). The bottom sealing ledge is in sliding insulating contact with the backward transfer limiter and divides the adjacent transferred volume of the backward transfer zone (D).

In the case of a reversible or convertible device, a preferred embodiment of the invention (FIG. 7) is that every point of every annular groove bottom between two adjacent vane chambers 7 is between two or more sealing ledges 23 and their ledges. For an embodiment of bottom unloading cavities and sealing ledges with one unloading cavity 22 at, in this case the bottom unloading cavity in the backward transfer zone is the closest two vanes of the two bottom sealing ledges. Separated by sliding insulating contact with the backward transfer limiter 21 of the chambers 7. In this case, the local pressure balancing means includes a rotor through which all the bottom unloading cavities 22 connect to the force chamber 6 which is closest and variable in length with regard to closest angular distance. Channels 24 of the working part of the apparatus. An embodiment of the channels 24 is also provided until their cross dimensions are similar or equal to the dimensions of the bottom unloading cavities. In the latter case, the bottom unloading cavities are bounded by the walls of the channels.

In the case of a device having a fixed position of cavities with high pressure on the inlet and outlet ports, every point of the annular groove bottom between two adjacent vane chambers has one unloading cavity and the bottom unloading cavity of the forward transfer zone. A sealing ledge bonded to the first vane chamber of the two vane chambers having vanes separating the high pressure cavity and the unloading cavity is connected to the second vane chamber. 7 shows, for example, the vane sealing ledge 17 and the adjacent bottom sealing ledge 23 which are as close to each other as possible at adjacent points of the corresponding surfaces.

In the embodiment described for the bottom unloading cavity and sealing ledge, force chamber dimensions can be selected to maintain axial balancing of the operating parts of the rotor in both transfer zones. Moving the center of the pressure force exerted on the actuating part of the rotor from the actuating cover plate side of the housing generates a variable pressure force moment that attempts to rotate the actuating part of the rotor about an axis perpendicular to the rotor rotational axis. Thus, the force chambers are located with a shift so that the force moments occurring in the forward and backward transfer zones compensate each other.

In order to provide a seal between the face surface of the actuating part of the rotor and the corresponding surfaces of the actuating cover plate of the housing, the actuating part of the rotor weakly presses on the sealing element of the actuating cover plate of the housing. It is reasonable to choose the shape and dimensions. In order to provide the necessary compression, the sum of the cross-sectional areas of all the force chambers of varying lengths is determined by the operating part of the rotor with respect to the joining properties of the sliding insulating contact between the working cover plate of the housing and the working part of the rotor and the values that depend on the area. The overhang area of the annular groove with respect to the plane perpendicular to the axis of rotation should be exceeded. For example, in the case of a flat clearance between the sliding insulating contact surfaces, at least 50% of the sliding insulating contact zone must be added to the annular groove projecting zone to calculate the pressure force balance. When calculating the sum of the protruding regions of the annular groove for the non-flat insulating surface and the clearance between the sliding insulating contact surfaces, the coefficient multiplied by the sliding insulating contact region between the operating cover plate of the housing and the operating part of the rotor is empirical. Can be determined.

The minimum required value above the zone is determined taking into account the elasticity of the resilient element of the force chamber, which is variable in length and frictional losses that must be overcome in order to provide the required alternating movement of the rotor and the support parts. The friction loss includes the friction force at the sliding insulation contact point between the embedded element of the force chamber and the rotor element, which transmits torque, such as a joint with the same angular velocity.

Rotor  support part Balancing  Maintain: Support Cavity and  Local pressure Force Balancing  Way.

The support part of the rotor (4 in FIG. 1B) is exposed to symmetrical forces from the side of the force chambers 6 with varying axial lengths to the corresponding surface of the support cover plate 5 of the housing. Thus, the actuating and supporting parts of the rotor move and fall off to come into contact with the corresponding sealing surfaces of the housing.

Each of the variable length force chambers 6, including the force chambers opposite the forward transfer limiter 15 or the backward transfer limiter 21, is characterized by the local pressure force balancing means of the actuating part 1 of the rotor. The nearest support cavity 25 confined between the cavity of the closest working chamber 2 and the support end surfaces of the support part 4 of the rotor and the surfaces of the support cover plate 5 of the housing 5. Hydraulically connected).

Local pressure force balancing means in the present invention means a set of channels, the cavities communicating with each other, through which force chambers of variable axial length are hydraulically applied to the cavity of the position and the support cavity of the position, respectively through it. It forms one manifold of the various hydraulic circuits connected to it. In this case the pressure of the force chamber in terms of hydraulic balancing of the operating and supporting parts of the rotor is from any cavity or force chamber that can be tolerated at any angle of rotor rotation and in terms of volumetric efficiency of the hydraulic system. For one leak it is generally the same as the corresponding pressure of the cavities hydraulically connected to the force chamber. The channels and cavities can be made in both the rotor and the housing. In the latter case, the channels and cavities of the housing are connected to the channels and cavities of the rotor during rotor rotation.

For various embodiments of the device with a housing force closure described below, the preferred embodiment of the present invention provides a local pressure force balancing means implemented by the channels and cavities of the rotor (FIG. 5B). In this case the hydraulic circuit of the local pressure force balancing means is provided by means of the channels of the working part of the rotor, for example connecting the annular groove 2 of the working part 1 of the rotor with the force chamber 6 of variable axial length. And vanes 8 directly connected to the force chamber 6 and channels 18 in the vane chambers 7 and through channels 26 of the force chambers 6, including force chambers. It also includes the channels 27 of the support part of the rotor connecting 6 to the support cavities 25.

In various embodiments of a device with a rotor force closure described below, a preferred embodiment of the present invention is a combination of channels and cavities of a rotor with channels 27-1 and a cavity 25 in a housing. Local pressure force balancing means (in this case connecting the annular groove of the working part of the rotor to the supporting cavities between the support cover plate 5 of the housing and the support part 4 of the rotor) (FIGS. 5C, 5D, 5E). ).

In a preferred embodiment of the invention, the support cavities 25 are made in the support part 4 of the rotor. In FIGS. 5B, 8A and 8B, the support cavities of the support part of the rotor are connected to the force chambers 6 inside the rotor with the channel 26 in the connector 12 by channels 27 or 27-1. . Thus, the pressures of all the supporting cavities operate with the pressure of the corresponding force chamber and the operating part of the rotor whose shaft length varies independently of the sealing surface defects, the clearance size of the end sealing and the corresponding leakage from and between the supporting cavities. It always matches the pressure of the corresponding cavity of the chamber. The leak depends on the bonding properties of the sliding insulating contact with the supporting cover plate of the housing and the insulating means of the supporting cavities of the supporting part of the rotor. These insulating means of the supporting cavities comprise an insulating dam 57 between the cavities; Their joining properties to the housing support plate determine the leak between the support cavities and the peripheral end sealing portions 58, and their joining properties to the housing support plate determine the leak from the support cavities to the outlet (FIG. 1B). .

The position, shape and area of the support cavities 25 at the outer end of the support part of the rotor, taking into account the sliding insulating contact area between the support cover plate of the housing and the support cavity insulating means, the pressure distribution therein, The pressure force applied to the support part of the rotor from the variable length force chamber is generally balanced by the pressure from the support cavities, so that the lower part of the support part of the rotor relative to the corresponding sealing elements of the housing required for insulation It is selected to leave only pressure. Thus, the support cavities actually serve to unload the support part of the rotor. The present invention also provides an embodiment having support cavities directly connected to a force chamber of varying length.

In order to provide the required insulation pressing of the support part of the rotor against the support cover plate of the housing, the total cross-sectional area of the force chambers of variable length is multiplied by the total weight ratio of the total insulation means of the support cavities. Combined, the total area of the support cavity projection in the plane perpendicular to the axis of rotation of the support part of the rotor exceeds the total area, where the corresponding weight ratio is the average of the rotor rotation angle area and the sliding of the support plate of the housing and the support part of the rotor. It depends on the average of the bonding properties of the insulating contact surfaces (e.g., 50%, for flat surfaces, as described above for the working part of the rotor). The required minimum zone excess also depends on the elasticity of the elastic elements of the force chambers and the frictional forces described above which must be overcome for the necessary mutual movement of the actuation and support parts of the rotor.

For embodiments of the device as a hydraulic motor or pump that operate at a range of rotational speeds and suction pressures that do not create cavitation in the vane chamber at the selected vane movement type, the support cover plate may not have a cavity. In the following, the deformation of the cover plate of the housing to reduce the cavitation possibility by dispersing the cavities will be described.

The number of support cavities of the support part of the rotor is equal to or multiples of the number of vane chambers of the operating part of the rotor.

In a preferred embodiment, the number of support cavities is equal to the number of force chambers of varying length and the number of vane chambers of the working part of the rotor, the support cavity area and the sliding insulating contact of the support cover plate of the housing of the corresponding insulating means. The sum of half of the area of is equal to the sum of half of the sliding insulation contact area with the actuation plate of the housing of the insulation means corresponding to the area of the opposing cavity formed in the annular groove of the acting part of the rotor of the backward transfer zone.

In a special case, the support part of the rotor has one annular groove with the vanes in the vane chambers. The vane blocking annular groove divides the annular groove into separate support cavities, the local pressure of which is balanced by the local pressure of the corresponding cavities of the force chambers and the corresponding cavities of the working chamber by local pressure balancing means. To achieve.

In this case, the surface of the support cover plate may include forward and backward transfer limiters. A second working chamber is also formed in the annular groove between the support part of the rotor and the support cover plate of the housing. The second working chamber can be made symmetrical with the first working chamber as described in US Pat. No. 33,48494 or asymmetric as described in Russian patent RU 2215903. In the latter case, the rotor device can perform a reversible action, ie change the direction of fluid flow without changing the input shaft rotation direction. The term symmetric is considered to be the symmetry of the pressure forces at all rotor positions. The size of the second annular groove may be different from the first annular groove on the premise of the balance of the support parts of the rotor described above. Insulating means of the support cavity include vanes whose surfaces slide along the forward transfer limiter of the support cover plate of the housing, and backward transfer insulating means of the rotor sliding along the backward transfer limiter of the support cover plate of the housing. do. Similar to the actuating part variant of the rotor described above, the vanes of the actuating part of the rotor may include vane unloading cavities and vane sealing ledges, and the rotor's backward transfer insulating means may include vanes or similar bottom unloading cavities. And an annular groove bottom of the support part of the rotor with the bottom sealing ledges.

For devices with both annular grooves and vane chambers on both parts of the rotor and transfer limiters on both cover plates of the housing, the definition of the “actuating” and “supporting” parts for the rotor parts is a conventionally used definition. Used for unity of terminology.

The present invention also provides an embodiment in which there are several pairs of forward and backward transfer limiters on the working cover plate of the housing. Each limiter pair thus further forms a pair of suction and pumping cavities in an annular groove connected to the inlet and outlet ports. The vane drive mechanism of this multicycle device is configured such that when the rotor rotates once, all the vanes are each carried out in every repositioning cycle with respect to the annular groove and many pairs of limiters are made on the working cover plate of the housing.

The multi-cycle embodiment is applicable to an apparatus with two annular grooves (in the operating and supporting parts of the rotor) described above. In such a device, the working cover plate and the supporting cover plate of the housing have the same number of backward and forward transfer limiters. The present invention provides both symmetrical and asymmetrical positions of the suction and pumping cavities formed in the annular grooves in the actuating and supporting parts of the rotor.

Thus, in the case of the bonding properties of the surface of the sliding insulating contacts which are not affected by the leakage determined by the sealing surface bonding properties, the variable fluid of the working fluid from the corresponding cover plate of the housing applied to the actuating and supporting parts of the rotor The pressure force is generally balanced by the same variable pressure force of the working fluid applied from the force chamber. The small compression required for the end sealing can be properly maintained very small.

The local pressure balancing means implies channels 27 with a wide flow zone and low hydraulic resistance, which is practically impossible to interfere with the suspended fine particles and the effect of the suspended fine particles of the working fluid on the pressure force balance described above. Remove it. In a particular embodiment of the invention, the cross sectional dimensions of the channels 27 are the same as or similar to the cross sectional dimensions of the support cavities 25.

Due to the above characteristics of the local pressure force balancing means, the balancing of the rotor parts is large, no matter how large the dispersion of the distributed local pressures in the transferred volumes, for example, due to local defects in the insulating surface due to wear. It is not disturbed.

One of ordinary skill in the art can see that the sliding insulating contact area can be significantly reduced by eliminating the cause of severe balancing imbalances. In a preferred embodiment of the present invention, the total area of the total projection of the sliding covering contact of the supporting cover plate and the insulating means of the supporting cavities of the supporting part of the rotor about a plane perpendicular to the axis of rotation of the rotor is the area of the supporting cavities. Significantly less than the sum; The total area of the working cover plate of the housing with respect to the plane perpendicular to the rotor rotational axis and the projection of the sliding insulating contact of the working part of the rotor is significantly smaller than the area of the projection of the annular groove of the working part of the rotor with respect to the same plane. Thus, the distribution of pressure changes in clearances in the clearance of the sliding sealing contacts of the rotor parts and the cover plate of the housing in the event of a local defect, however, is such that for the pressure force balance applied to all the rotor parts anyway. The impact of change is small.

If a distribution suction cavity is implemented on a support cover plate opposite the suction cavity, the hydraulic pressure of the suction cavity 28 of the working chamber through the other vane chamber or through the channels of the rotor or housing to the corresponding vane chamber as the distribution suction cavity. By providing a positive connection, the suction cavity lowers the tendency for cavitation. In the suction cavity, several vanes are at different stages of acceleration or slowdown at the same time as shown in FIG. The vane chambers 7 of the suction cavity are connected to the distribution suction cavity 28-1 via the force chamber 6, and consequently to the support cavities 25 of the support part of the rotor by channels 27. Connected to create a through hydraulic circuit. The hydraulic resistance of the channel 27 and other components of the hydraulic circuit is low. Thus, in this case the channels 18 of these vanes are connected in parallel using a dispensing suction cavity. The fluid reduces the pressure drop in the vane chamber by flowing through the vane chamber of the high axial speed vane through the channels of the low axial speed vane rather than the channels of the high axial speed vane. In this case, the degree of increase in the maximum self suction speed depends on the number of vanes simultaneously in the suction cavity. If the channels are made in the rotor between vanes and not inside the vanes, the effect of fluid redistribution flowing into the vane chamber to replace vanes protruding through the parallel channels and the distribution cavity is the same. The ability to increase the maximum self-suction rate several times is an important advantage of pumps with distribution cavities. Connecting the distribution cavity and the suction port by one channel in the housing further increases the ultimate rotor rotation speed without cavitation. If the dispensing pumping cavity is made on the opposite side of the pumping cavity and connected to the pumping port by the channel of the housing, the hydraulic loss of the pump is reduced.

Another way to overcome the tendency of cavitation and increase the ultimate self-suction rate is to change the vane movement type. If the vane's axial movement is replaced by vane rotation around a certain axis (e.g., an axis parallel to the rotor rotation axis), vane channels or parallel channels for inplace the turning vane. And the fluid flows around it in a wide vane chamber without significant pressure drop. To implement this means, it is convenient to use a hydraulic device with a rotor force closure rather than a housing. The following is a more detailed explanation of the differences between the two architecture types and a sample that implements such vane movement.

housing Force With closure  Strain relief chamber .

The above description relates to an embodiment of the rotor device in which a rotor is made between the operation and support face cover plates of the housing and the working chamber and support cavities are made on the outer face surfaces of the rotor. The axial pressures of the working fluid applied to the rotor and each rotor part (actuating part and support part) are balanced with each other and pressurize each rotor part. For steel devices, compression deformation can be ignored. In such a device, the axial component of the fluid stretching pressure force is applied to the housing. In the present invention, such a structure is referred to as a rotor device with a housing force closure.

The pressure force acting on each cover plate from inside the rotor device is not balanced from the outside due to the back pressure force. If the pumping pressure is high, the elements of the housing and coverplates connecting the cover plate and the cover plate are deformed and start to affect the quality of the face seal. The present invention provides a hydrostatic means to prevent the insulating surface deformation of the housing cover plates in order to prepare for high pressure.

In one embodiment of the hydrostatic means (FIG. 10), the face cover plates of the housing correspond to two elements, namely the rotor part corresponding to the external load bearing element 29 which bears the pressure force of the working fluid on its own. And an internal functional element 30 in sliding insulating contact with. Between these elements opposite the pumping cavity is created a strain relief chamber 31 which is connected to the pumping cavity via a channel 32. The shape, dimensions and position of the deformation leaving chamber are selected to compensate for the fluid pressure force of the internal functional element 29 in the housing cover plate from the rotor side by the fluid pressure force from the deformation prevention chamber 31 side. As a result, the external load bearing element 29 of the cover plate is subjected to a pressure force and a deformation by the pressure force. Internal functional elements unloaded from the working fluid pressure force are not deformed and maintain the shape of the sealing surface and the quality of the seal. The strain relief chamber 31 is sealed along a perimeter so that no leak occurs in the chamber even if the load bearing element 29 of the cover plate is deformed.

The element connecting the housing cover plate and the housing force closure of the rotor device can be made in two embodiments. The first embodiment provides a linking element as a hollow body, such as a barrel, with a space between the cover plates (FIGS. 2A, 2B). The present invention also provides a housing (FIG. 2C), such as a bobbin, in which the linking element 33 of the housing is mounted to the bearing 34 and passes through the rotor interior between the face cover plates 3, 5 of the housing, The cover plate is connected to the linking element 33 of the housing via a tightening nut 35.

Rotor Force Closure .

There is also another embodiment of a hydrostatic means for preventing deformation of the ising surfaces of the rotor force closure and the housing sliding insulating contacts of the rotor device. The rotor takes the radial components of the working fluid pressure force in the annular groove, making it sufficiently robust and robust.

The device with the rotor force closure provides the operating part of the rotor by combining the actuating and supporting cover plates of the housing into an operational unit of the housing between the operating and supporting parts of the rotor. The operating face surface of the sliding face is in sliding insulating contact with the operating cover plate surface of the housing operating unit, and the supporting face surface of the support part of the rotor is in sliding insulating contact with the supporting cover plate surface of the housing operating unit.

The housing operating unit can be made an integral part. In this embodiment, the function of the actuating cover plate is performed by its face surface of the actuating unit in sliding insulation contact with the actuating face surface of the actuating part of the rotor, the function of the actuating cover plate being the support face surface of the support part of the rotor. It is carried out by means of the opposing face surfaces of the operating unit which are in sliding and insulated contact. The corresponding parts of such a housing operating unit are then regarded as the operating and supporting cover plates of the housing.

The present invention provides in such an embodiment a stretching pressure force of a working fluid which attempts to push the actuating and supporting part of the rotor from the cover plate of the housing actuating unit to the rotor elements assembly described above kinematically connecting the actuating and supporting part of the rotor. Ensure that one rotor linking source is transferred. The linking element may be connected to both parts of the rotor via force chambers of variable length, or may be connected to one of the rotor parts via the force chambers and firmly coupled to the other rotor part.

In one embodiment of the invention, the rotor is similar in shape to a bobbin having two separate parts 36 of large diameter connected by a small medium part of the rotor linking element 37. (FIGS. 2D, 2E, 2F, 2G). The working chamber is on the inner face surface of one part or both parts of larger diameter.

Pumping and suction of the working fluid is realized through the channels in the housing operating unit 38. In the case of an embodiment of a submersible pump, there can be no suction channel. The outer face surface of the actuating unit performs the same function as the inner functional element of the actuation and support cover plates of the housing in pumps with the housing force closure. At least one of them is a backward transfer limiter and a forward transfer limiter.

In such an embodiment, the rotor has two parts movable relative to one another: an operating part 1 comprising a vane chamber 7 with vanes 8 and an annular groove 2, and a support cavity 25 Or, in the case of an embodiment with two working chambers, can be similarly constructed with a support part 4 comprising annular grooves and vanes. The first of the rotor parts is firmly coupled to the rotor linking element, for example made of a rigid bobbin, and the second part is placed in the middle part of the rotor linking element and through a variable length force chamber. It is made of annular elements that connect to the first part. FIG. 2D shows an apparatus in which the actuating part of the rotor is made of annular element, and FIG. 2G shows an apparatus in which the support part of the rotor is made of annular element.

FIG. 2E shows an embodiment of a rotor in which two parts of the rotor have two working chambers and two sets of vanes, one of which is made of an annular element. Both cover plates of the housing, which are both face surfaces of the housing operating unit 38, have a forward transfer limiter 15 and a backward transfer limiter 21. In this case, the definitions of “operation” and “support” for the rotor parts and the housing cover plates are also relative and are used to unify the term.

2F shows a rotor embodiment with separate carrying elements 39 of the rotor made of bobbins. The actuating part 1 and the support part 4 of the rotor are mounted to the intermediate link part of such a carrying element. In this case, the variable force chambers 6 can be made between the inner faces of this third conveying element and one or two parts of the rotor (actuation or support part).

In such a device, the stretching components of the pressure force of the working fluid take over those rotor parts that are sufficiently sufficiently rigid that they do not affect leakage with deformation.

In the case of a device with a rotor force closure, it is difficult to exchange working fluid between the working chamber and the vane chamber using the support part of the rotor, because of the long and complicated shape of the inner channel of the rotor required for it. Therefore, in the case of such a machine, it is reasonable to overcome the tendency of cavitation by changing the vane movement characteristics and vane shape.

2g shows an embodiment of a device in which the acting part of the rotor is made of bobbins. In such a structure, to position the vane drive mechanism, it is possible to use the rear face of the actuating part 1 of the rotor and the housing part 40 adjacent thereto. The vanes 8 are in the vane chamber 7 of the operating part 1 of the rotor and can rotate about an axis 41 parallel to the rotor axis of rotation 9. Each vane has an axial ledge 42 passing through the rear face of the actuating part 1 of the rotor. The shaft ledge 42 has a pivoted arm 43 which slides when rotating the rotor in the cam guiding slot 44 and rotates the vanes so that the vanes close the annular groove 2 in the forward transfer region. In the backward transfer zone the vanes move from the annular groove into the vane chamber 7. The flow of fluid produced by the vane rotation does not cause a significant pressure force drop that can cause cavitation. In such a structure, the working chamber can be deepened to increase the displacement in the same dimensions. Increasing the ratio of the working chamber depth to the sealing surface diameter of the rotor and housing results in reduced frictional losses in the total power and consequently the efficiency of the hydraulic system.

The housing operating unit of the device with the rotor force closure is subject to the symmetrical pressure force of the fluid and is generally balanced so that it is an efficient means of preventing the deformation of its surfaces of sliding insulating contacts. The type of mounting it in the housing must allow fluid to enter and exit the pump operating chamber and prevent the rotation of the operating unit relative to the housing about the rotor rotation axis (the housing itself can rotate about the rack of the entire hydraulic system). have).

In order to maintain the balancing of the cavity pressure between the housing operating unit and the rotor parts, the support cavities 25 of the support part 4 of the rotor, the force chambers 6 inside the rotor, the vane chambers 7 and Included in the device is a channel connecting the cavities of the working chamber. These channels can be made in the rotor to pass through the intermediate rotor linking part. A preferred embodiment for an apparatus with a rotor force closure provides channels 27-1 to the operating unit 38 of the housing, including a forward transfer limiter and a backward transfer limiter. In this case, the through channel 27-1 of the housing operating unit 38 in the transfer zone should be made to block the working fluid flow between the transferred adjacent volumes and the suction and pumping cavities. That is, the vane sealing ledge 17 or bottom sealing ledge 23 in sliding insulating contact with the insulating surface of the corresponding transfer limiter is passed through the corresponding channel 27-1 of the operating unit 38 through a corresponding point. ) And the channel of the forward transfer limiter 15 or the backward transfer limiter 21 closed at the bottom of the annular groove 2 or the surface of the vane 8 on the working part 1 side of the rotor at the same time, It is closed by sliding insulating contacts of the support cover plate 5 of the housing operating unit 38 of the support part 4.

The invention also provides an embodiment of the device in which there is a rotor force closure and the support cavity 25 is made on the support cover plate of the operating unit 38 of the housing, not on the support face of the support part 4 of the rotor. (FIGS. 5C, 5E, 5F). The support cavity insulating means of such an embodiment includes partitions between the cavities in the housing and also its joining properties to the support parts of the rotor, whose joining properties to the support parts of the rotor determine leakage between the support cavities. It includes a peripheral insulating surface that determines leakage from the support cavity to the outlet.

The position, shape and area of these support cavities on the support cover plate of the housing operating unit, and the pressure distribution therein, taking into account the sliding insulating contact area with the insulation means of the rotor with the support part of the rotor, the pressure distribution therein, The pressure force of the working fluid contained in the variable force chambers, which presses the wedge towards the support cover plate of the housing operating unit, only slightly compresss the corresponding sealing elements of the housing as necessary for the supporting part of the rotor to insulate. Is generally selected to maintain balancing with pressure from the support cavities side.

The radius of this cavity is selected to provide said alternative balancing of the support part of the rotor, and the corresponding arc dimension is chosen to prevent working fluid leakage between the transferred adjacent volumes and the suction and pumping cavity. That is, the insulating surfaces of the support part 4 of the rotor, including the dam (FIG. 5e) between the insulating surface of the housing operating unit 38 and the channel 27 in sliding insulating contact, pass through the corresponding point. The support cavities 25 of the operating unit 38 must be completely closed. In the embodiment shown in FIGS. 5C, 5F, there may be no cavity at the support face surface of the support part 4 of the rotor. The support cavities 25 in the support cover plate of the housing actuating unit are connected with the adjacent cavity through the channel 27-1 by angular distance cavities in the actuation chamber of the actuating part 1 of the rotor. Hydraulically connected, each made in the forward transfer limiter 15 and the backward transfer limiter 21 and blocked by the annular groove 2 bottom or vane 8 surface from the operating part 1 side of the rotor. The channel 27-1 is connected to the support cavity 25, which is simultaneously closed by sliding insulation contact with the support cover plate 5 of the housing operating unit 38 of the support part 4 of the rotor. do.

In a particular embodiment of the invention the cross sectional dimensions of the channels 27-1 are the same as or similar to the cross sectional dimensions of the support cavities 25 (FIG. 5E).

Another embodiment of a device with a rotor force closure made of a hollow body (barrel) rather than a bobbin is also possible (FIG. 2H), which is made of a hollow cylinder 45 connecting the individual face parts 46 of the rotor. A rotor linking element 37 comprising an intermediate part is included to form a space in which the housing operating unit 38 is mounted. In this case, the housing operating unit is mounted to the housing using a shaft 47 through which the shaft passes through one of the individual face parts 46 of the rotor. Such a solution proposed for the rotor is similar to the solution proposed for the bobbin rotor.

The pressure of the working fluid contained in the variable-length force chamber 6 moves the operating part 1 and the support part 4 of the rotor close to each other and balances the pressure so that the housing operating unit 38 or each other It is also possible to connect the support and actuation parts of the rotor directly to the corresponding set of force chambers to push out the corresponding parts (FIG. 2I).

As described, it is possible to maintain hermiticity in the alternating movement of the rotor part, including its tilt to the force chambers of variable length, so that when the force chambers of the rotor of such a device are mounted on an actuating or supporting part on the opposite side of the housing operating unit In addition to its main function, it serves to prevent deformation of the insulating surface of the corresponding rotor part under the influence of the axial components of the working fluid pressure force, similar to the deformation chamber of a device with a housing force closure. Thus, the pressure forces deform the outer part of the rotor linking element supporting the force chamber, and such deformation is insignificant in the insulating.

In the case of a structure with a rotor force closure, the rotor becomes complicated, but the housing structure can be greatly simplified and lightweight. This may be important when such a structure is used, for example, as a pumping motor unit mounted on a mechanical transmission in which there are two or more engines in which both the rotor and the housing must rotate relative to the rack of the assembly. Changing the position and vane movement characteristics of the vane drive mechanism at the rotor outer face can improve the relative depth of the working chamber and device efficiency and eliminate the source of cavitation in the vane chambers.

In the embodiment of the invention described, the means for maintaining local pressure balancing includes a set of channels of the rotor, and in some embodiments the housings, in particular the channels of the housing operating unit. According to the structure of a particular embodiment of the invention, the channel set in the rotor has a channel connecting variable force chambers with annular grooves of the operating part of the rotor or channels connecting variable force chambers with support cavities. Or a combination of channels or listed channels connecting the support cavities with the annular groove of the actuating part of the rotor. The rotor channels may include vane chambers, vane channels and force chamber channels.

The invention also provides an embodiment in which a force chamber of variable length is directly connected to the annular groove (FIG. 5F) or the support cavities (FIG. 2J). In the latter case, the holding elements in the form of force cavities 14 of the operating part 1 of the rotor directly connected to the annular groove 2 of the operating part 1 of the rotor, the supporting part 4 of the rotor Embedded elements in the form of connectors 12 disposed in the force cavities and the force cavities 14 of the support part 4 of the rotor directly connected to the support cavities 25 between the support cover plate 5 and the support cover plate 5. An embodiment of an apparatus with varying length of force chambers 6 is provided. In such an embodiment, the means for maintaining local pressure balancing include openings of the rotor (48 in FIG. 2J) formed by direct connection of the force chamber 6 and the annular groove 2, the channel 26 of the connector 12. And openings 48-1 formed by the direct connection of the force chamber 6 and the support cavity 25. In an embodiment of such a device with a rotor force closure, the means for maintaining local pressure balancing may include annular openings 48 and annular openings of the rotor formed by direct connection of the annular grooves 2 of the force chamber 6 as described above. Included are channels 27-1 of the operating unit 38 of the housing connecting the groove 2 to the support cavities 25.

suggestion Solution  summary

As above, the key to the described solution to eliminate the sources of dissipated energy loss due to friction and cavitation of face seals is as follows.

The rotor consists of an actuating part and a support part connected through force chambers of varying lengths so that when the length of the force chamber is changed, it provides a sliding insulation contact with the corresponding sealing surface of the operation and support cover plates of the housing. This results in some mutual axial movement and tilt of the working and supporting parts of the rotor as required. Support cavities are made between the support cover plate of the housing and the support part of the rotor.

The means for maintaining local pressure balancing is equal to the pressure of the cavities of the working chamber and the corresponding support cavities, regardless of the bonding properties of the surfaces of all sliding insulating contacts and the leaks associated therewith. To provide. Since the shape, dimensions and position of the force chambers and the supporting cavities can be selected, a symmetrical distribution close to the reflection of the pressure force acting on the opposing faces of both parts of the rotor and maintaining balancing of each of the parts at the corresponding position (a close to reflection symmetric distribution) is formed. Compression of the rotor parts against the housing cover plates necessary to provide insulation to the face seals can be made to any small level within a reasonable range. The identity of the pressures that determines this pressing is not disturbed by changing the bonding properties of the surfaces of the sliding insulating contacts, in particular by the occurrence of local defects of the sealing surfaces.

In this case, one of the units, either the rotor or the stator (mostly referred to herein as the housing), takes over the compression pressure forces of the working fluid by itself, while at the same time the other unit is made to receive the compression pressure forces of the working fluid. The elements deformed under the influence of the axial pressure forces in the unit receiving the stretching pressure forces of the working fluid are separated from the elements with flat surfaces which provide sliding insulating contact by passing the pressure.

In pumps with a housing force closure, fluid is sucked into the vane chambers and the force chambers through the channels of the support part of the rotor and the distribution cavity in the support cover plate of the housing.

The channels have a wide flow cross section so that the pressure due to the fluid flow does not cause a significant pressure drop and is not affected by suspended particles.

The outer face of the pump rotor with rotor force closure can be used to create a vane drive mechanism that rotates the vane so that the pressure in the vane chamber is not significantly reduced.

One of the present invention Example  Detailed description of

In order to explain in detail the structure and operation of one embodiment of the invention, a rotor sliding vane device with a force closure to the housing in the form of a hollow cylinder (" barrel ") and a working annular groove An embodiment of the present invention will be considered.

The rotor sliding vane device (FIGS. 1A, 1B, 2A, 2B, 9, 10) of the embodiment of the present invention comprises two main units; That is, it comprises a housing and a rotatable rotor installed inside the housing.

The rotor includes an actuating part 1 having vane chambers 7, the vane chambers having vanes 8 made on the actuating face surface of the actuating part and having through channels 18. An annular groove 2 of a constant rectangular cross section is included which is connected to the vane chambers 7.

The housing 40 consists of an inlet port 49 and an outlet port 50 and face actuating and supporting cover plates 3, 5, each plate comprising a load bearing element 29 and an internal functional element 30. It consists of. In addition, the outlet port is made between the load bearing and functional elements and the suction and pumping distribution cavities 28-1 and 51-1 divided into insulating dams 57 made in the functional element of the support cover plate. There are strain relief chambers 31 connected to 50.

The working chamber of the device is bounded radially by the inner surfaces of the annular groove 2 and axially by the inner surface of the working cover plate 3 of the housing and the bottom 20 of the annular groove. In the working chamber, a forward transfer limiter 15 and a backward transfer limiter 21 are formed, an intake cavity 28 is formed and connected to an inlet port 49, and a pumping cavity 51 is formed to form an outlet port ( 50). The suction and pumping cavities are correspondingly connected to the inlet and outlet ports via channels 52 and 53 of the operating cover plate 3 of the housing, respectively.

In consideration of the process occurring in the device during the transfer of the working fluid, it is divided into four areas: suction area A, forward transfer area B, pumping area C and backward transfer area D. FIG.

The suction area A corresponds to the position of the suction cavity 28 and the pumping area C corresponds to the position of the pumping cavity 51. The forward transfer region B is located between the suction region A and the pumping region C. In this region, the fluid contained in the working chamber between the vanes 8 and the rotor cavities connected to the working chamber is transported from the suction zone A to the pumping zone C. In the backward transfer area D, part of the fluid from the pumping area C is conveyed back to the suction area A.

The forward transfer limiter 15 is mounted to the operating cover plate of the housing, located in the operating chamber of the forward transfer area B, and in sliding contact with the face surface of the vanes 8 moving to the annular groove 2, It provides the possibility of separating at least one vane inner cavity 62 from the suction cavity 28 and the pumping cavity 51 by vanes.

In another embodiment of the present invention, the limiter can be made movable in the axial direction. When moving in the axial direction, the cross-sectional area of the working chamber in the forward transfer region changes and thus the displacement of the device. To control the axial movement of the device, the drive mechanism of the forward transfer limiter is required. In the case of a fixed displacement device, the forward transfer limiter may be made as a flat insulating point on the working cover plate of the housing.

The backward transfer limiter 21 is mounted on the operating cover plate 3 of the housing, located in the operating chamber of the backward transfer region D, and the rotor insulation means of the backward transfer, i.e. the annular groove 2 The suction cavity 28 and the pumping cavity 51 of the working chamber are separated by sliding contact with the inner surface of the.

The vane drive mechanism 54 is made of a cam mechanism mounted to the carrier 40 of the housing 40 of the guide cam slot 44 in which the side lobes 56 of the vanes 8 slide therein. . The profile of the cam slot determines the axial movement characteristics of the vanes upon rotor rotation. The vane drive mechanism controls the periodic movement of the vanes 8 with respect to the operating part 1 of the rotor as it rotates so that the vanes 8 of the suction area A are annular grooves 2 from the vane chambers 7. Moving in the axial direction, in the forward transfer area B closes the cross section of the working chamber, in the pumping area C exits the annular groove 2 from the vane chambers 7 in the backward transfer area D. Open the cross section of the working chamber.

The forward transfer limiter 15 is formed with an unlocking section with a slot 63 (FIG. 1B). The dimensions and position of this slot are selected to provide pressure force balancing at the vanes' faces by initiating an axial movement from the annular groove into the vane chamber.

Other embodiments of the invention may have other vane movement characteristics. All types of vane movements with respect to the rotor which periodically change the closing angle of the cross section of the annular groove are acceptable. For example, in addition to the axially moving structure, radial and rotary vanes are possible by means of movement and a combination of such movements. In the case of pumps of variable displacement, the mechanism must be kinematically connected to an axially movable forward transfer limiter to move from the vane chambers to the annular groove, corresponding to a change in the cross-sectional area of the working chamber in the forward transfer region. It can provide a change in the angle of the vanes.

The rotor also comprises a support part 4 having support cavities 25 at the outer face (FIG. 1B). The support cavities are insulated with support cavity insulation means, ie with the flat surface of the dam 57 and the peripheral face seals 58, which insulates the flat of the functional element 30 of the support cover plate 5 of the housing. This is possible because the surface and the flat surface are in sliding insulating contact.

The actuating and supporting parts of the rotor are mounted on bearings 34 in the actuating cover plate 3 and the support cover plate 5 of the housing, respectively, and are connected to the inlet shaft 60 by means of joint means 61. , At the same time rotating but hardly rotating in the axial direction, for both parts of the rotor are inclined relative to each other at least sufficient to provide sliding insulating contact with the corresponding cover plates of the housing.

The rotor also comprises a force chamber 6 of variable length, between the actuating part 1 of the rotor and the support part 4 of the rotor. In an embodiment of the apparatus, the force chambers are mounted with force cavities 14 made on the surface of the actuating part 1 of the rotor and the support part 4 of the rotor facing each other, and are mounted to slide in the force cavities. Formed by cannulated connectors 12. The cannulated connector has sealing shoulders 13. Their shape, position and dimensions are selected such that the force chambers are insulated within the entire range in which the support part of the rotor moves axially and inclined with respect to the working part of the rotor. Springs 59 are installed in the variable length force chamber to provide a seal in the absence of pressure. Changing the length of all the force chambers 6 equally shifts the actuating part 1 of the rotor and the support part 4 of the rotor alternately, and changing the length differently for each force chamber 6 causes the actuating part 1 of the rotor. ) And the support part 4 of the rotor.

In the local pressure balancing means of the embodiment of the apparatus, vane chambers 7, each of the cavities 28, 51 and 62 of the working chamber, pass through to be connected to the force cavities 14 of the working part of the rotor. The channels 18 of the vane, the channels 27 of the connectors 12 and the channels 27 through which the force cavities 14 of the support part of the rotor pass to connect to the support cavities 25 Included. The channels have low hydraulic resistance such that, at the flow rate of the working fluid through any of the channels corresponding to the maximum allowable leakage from the working chamber, the pressure drop in this channel is largely, for example, nominal ( nominal) several hundred times lower than the pumping pressure. Thus, in view of the balancing of the pressure force acting on the rotor parts at any rotor rotational angle, the local pressure in the support cavity of the force chamber and the cavity of the working chamber connected thereto is any allowable from said any cavity. Approximately the same as the leak level.

The vanes' faces moving into the annular groove have vane sealing ledges 17 closing the forward transfer vane inner cavities 62 in sliding contact with the forward transfer limiter.

The bottom 20 of the annular groove 2 has a bottom end which is connected to the force chambers 6 via the vanes and channels 18 of the vane chambers 7 in sliding contact with the backward transfer limiter. There are bottom sealing ledges 23 closing the loading cavities 22. In the present embodiment, the area of the sliding surface of the bottom sealing ridges 23 is equal to the area of the sliding surface of the vane sealing ledge 17.

The number of support cavities 25 is equal to the number of vane chambers 7. The support cavities 25 are oval and the radius width is equal to the radius width of the annular groove 2. The sum of the area of the support cavities 25 and the area of the dam 57 is equal to the area of the bottom of the annular groove 2. The areas of the sliding surfaces of the dams 57 are equal to the areas of the sliding surfaces of the bottom sealing ridges 23, and the insulating surfaces of the supporting cover plate 5 of the housing and the sliding insulation of the peripheral face seals 58. The area of the rating contacts is equal to the corresponding areas of the sliding insulation contacts of the actuating cover plate 3 of the housing and the actuating part 1 of the rotor. The support cavities 25 are located opposite the annular groove 2, and the dams 57 are located opposite the bottom sealing ridges 23.

The number of force chambers 6 that is variable in length is equal to the number of vane chambers 7. The cross section of the force chambers 6, which is variable in length, is circular. The sum of the cross sections of the force chambers 6 is the actuating part of the rotor than the sum of the area of the bottom of the annular groove 2 and the area of the sliding insulated contact of the actuating cover plate of the housing and the actuating part of the rotor. It is sufficient to press 1 and support part 4 small against the corresponding cover plates 3, 5 of the housing, and by a value sufficient for insulation.

The aforementioned device Example  action

The operation of the rotor sliding vane device described above as a pump, and the balance of the pressure force of the working fluid applied to the operating and supporting parts of the rotor will be described. The same argument holds true for hydraulic motors that have been modified to fit the hydraulic contact differences of the vanes described above. To take into account the entire cycle consisting of suction, forward transfer, pumping and backward transfer, one must consider a single transferred volume formed by cavities at transference connected to the vane chamber of one vane selected during movement. The first thing to consider is the position of the selected vane at the starting position of the suction area. The balance of the pressures applied to the rotor parts should be taken into account on the basis of constant local pressures at the sealing clearances adjacent to the transferred volume. This pump works as follows;

At the initial moment of the same period as one rotation of the rotor, the select vanes are located at the boundary of the backward transfer area and the suction area.

When the input shaft (60 in FIG. 2A) rotates, its torque is transmitted through the joints 61 to the actuating part 1 and the support part 4 of the rotor so that they rotate about the housing 40.

When the rotor is rotated (9 in FIGS. 1A and 2B), the vane 8 in the suction region A is in such a way that the side lobe 56 of the vane 8 slides along the guide cam slot 44. ) Moves to annular groove 2. Passes through the suction distribution cavity 28-1 of the support cover plate 5 and the channel 52, the support cavity 25 and the channel 27 of the support part of the rotor, and the cannulated connector of the force chamber 6 ( The working fluid passing through 12 fills the space in the vane chamber 7 emptied by the movement of the vanes 8. In addition, some of the fluid travels to the emptied volume of the vane chamber through the channels of the vanes 8 (18 in FIG. 9) and similar channels of the other vanes connected to the suction distribution cavity. The fluid moving in the vane chamber and filling the space of the vane chamber 7 emptied by the vanes 8 compensates for the volume replaced by the part of the vanes 8 of the annular groove 2. There is a distribution cavity 28-1 and channels 52, 27 of the support cover plate 5 of the housing so that fluid passes through the vane chamber 7 of the vane 8 when the vane 8 is moved. The hydraulic resistance of the duct can be reduced, thereby reducing the cavitation tendency of the pump and increasing the maximum self suction speed.

When the pressure of the working fluid contained in the force chamber is low or zero, the force cavities of the force chamber are slid off by a spring (59 in FIG. 2A). The protruding vanes of the forward transfer area B are brought into sliding contact with the forward transfer limiter 15 by their sealing ledges 17 and closed by the sealing ledges of the vanes 8 ′ from the front of the rotor rotation direction. It is closed from the back of the vane inner cavity (62 in FIG. 9) of the forward transfer. The insulating dam 57 of the support part of the rotor of the forward transfer region is in sliding contact with the flat insulating dam 64 of the support cover plates of the housing, so that the front dam 57 'is moved from the front of the rotor rotation direction. It is closed from the back of the support cavity 25 which is closed by it. The variable force chamber 6 is insulated to the sealing shoulders 13 of the cannulated connector 12. Thus, the vane inner cavity 62, the channel 18 of the vane 8, the vane chamber 7, the cavities 14 and channel 26 of the force chamber 6, the support part 4 of the rotor The currently transferred volume 65, including the volumes of the support cavity 25 and the channel 27, is closed in the forward transfer region.

When the rotor rotates, this currently transferred volume 65 moves from the suction region A to the pumping region C in the forward transfer region B. Due to the internal leakage of the working fluid between the transferred volumes as above, the transferred volume moves towards the pumping area, increasing the pressure therein. Pressure increasing properties are affected by rotor rotational speed, outflow pressure, and bonding properties of the insulating contacts (ie clearance between all sealing surfaces of the forward transfer area and the presence of local defects on the corresponding surfaces), which are different transferred volumes. May vary. However, due to the local pressure balancing means as one manifold of the channel 18 of the vane 8, the channel 27 of the support part of the rotor and the channel 26 of the cannulated connector 12, the selected transferred volume is selected. The pressures of all the cavities 62, 18, 7, 14, 27 and 25 forming the same are the same. As the fluid pressure in the force chamber 6 included in the transferred volume increases, the hydrostatic forces of the fluid become more important in the balance of the forces applied to the actuation and support parts of the rotor, the spring (Fig. 2A). 59) The importance of the role is less. The area of the sliding insulating contact with the operating cover plate of the housing of the operating part of the rotor determined by the dimensions of the annular groove 2, in this case the sealing shoulders (66 of FIG. 1 b) of the operating cover plate of the housing, and The dimensions of the force chambers 6 are such that the pressure forces of the fluid acting on the actuating part of the rotor from the vane inner cavities 62 side, the actuating part 1 of the rotor relative to the actuating cover plate 3 of the housing. It is chosen to be less than the pressure force from the force chambers 6 by a small value chosen to provide the minimum pressure required to compress. The value of the pressure force difference is selected in consideration of the frictional force of the joint couplings with the shaft of the force chambers and the rotor parts. Similarly, the dimensions and shape of the support cavities 25 of the support part of the rotor and the dimensions of the sealing shoulders (67 of FIG. 1A) of the support cover plate 5 of the housing are from the rotor from the support cavities 25 side. The pressure of the fluid applied to the support part of the force chambers 6 by a small value selected to provide the pressure necessary to press the support part 4 of the rotor to the minimum necessary for the support cover plate 5 of the housing. Smaller than the pressure forces from the side. The mutual position of the vane inner cavities 62, the force cavities 14 and the support cavities 25 is selected such that the moment of back pressure forces of the working fluid applied to the actuation and support parts of the rotor is minimized. Thus, the pressure forces applied to the actuating part of the rotor from the vane inner cavities side and the force chambers side are generally balanced. That is, they balance each other except for the small compression required for proper face sealing from the force chambers side to the working cover plate of the housing. The pressure forces applied to the support part of the rotor from the support cavities side and the force chambers side are generally balanced in a similar manner.

At the end of the forward transfer region, the sealing ledge 17 of the front vane 8 'moves to the unlocking section of the forward transfer limiter 15. At the same time, the partition 57 ′ in front of the support cavity 25 of the selected transfer volume moves from the insulating dam 64 to the region of the pumping distribution cavity 51-1 of the support cover plate 5 of the housing. do. Here, the selected transferred volume is connected to the pumping area.

The insulating dams between all the cavities of the selected transferred volume and the support cavities 25 of the support part 4 of the rotor are subjected to the pumping pressure through the pumping area C. Due to the above characteristics of the force chambers 6, the support cavities 25 and the sealing shoulders (66, 67 of FIGS. 1A and 1B) of the support cover plate 5 of the housing and the actuating cover plate 3, the vanes Pressure from the inner cavities 62 side and the force chambers 60 side to the actuating part of the rotor and the rotor 4 from the support cavities 25 side and the force chambers 6 side of the pumping region C The pressures acting on the support parts of) are also balanced with one another except for the minimum required for minimal compression on the corresponding cover plates of the housing of the rotor parts.

Due to such mutual balancing maintenance, the working part and the supporting part of the rotor are not deformed in the axial direction and the flat shape of the sealing surfaces is maintained.

Since their deformation is less affected by leakage than the deformation of the corresponding functional elements 30, the pressure forces of the fluid are actuated by the housing through the deformation prevention chambers 31 and the external load-bearing elements of the support cover plates. Is passed to (29). Such functional elements do not occupy a large part of the pressure forces required for pressing against the load bearing element. Their sealing surfaces remain flat to provide insulation.

When the selected vane passes through the pumping region, the side lobe 56 of the vane is guide cam slot 44 in such a way that the vanes of pumping region C move from the annular groove 2 to the vane chambers 7. Slid along. At this time, the working fluid passing through the channel 18 of the vanes 8 and the channels 26 of the cannular connectors 12 is removed from the vane chamber 7 occupied by the moving vanes 8. Displaced from the space to the outlet port 50 to compensate for the volume emptied by vanes in the annular groove. Thus, pump displacement is not affected by vane size.

In the backward transfer zone D, the selected vanes move completely into the vane chamber. The bottom sealing ridges 23 of the annular groove 2 adjacent to the vanes selected at the front and rear of the rotor direction of rotation move from the pumping area to the backward transfer area, where they are in sliding contact with the surface of the backward transfer limiter. To close the bottom cavity of the annular groove. The insulating dam 57 of the support part 4 of the rotor is brought into sliding contact with the flat insulating dam 64 of the support cover plate of the housing in the backward transfer region, so that the insulating dam 57 'in front of It is closed from behind the support cavity 25 closed from the front in the rotor rotational direction. The variable force chamber 6 is insulated with sealing shoulders 13 of the cannulated connector 12. Thus, the bottom unloading cavity 22, the channel 18 of the vane 8, the vane chamber 7, the cavities 14 and channel 26 of the force chamber 6, the support part 4 of the rotor The recurrent backward transfer volume 68, which includes the support cavity 25 and the volumes of the channel 27, is closed in the backward transfer region.

This current backward transfer volume 68 of the backward transfer zone D moves from the pumping area C to the suction area A as the rotor rotates. As the transferred volume moves towards the suction region, due to the internal leakage of working fluid between adjacent transferred volumes, the pressure in that zone is reduced. The nature of the pressure drop depends on the rotor rotational speed, the difference between the pumping and suction pressures, the bonding properties of the surfaces of the insulating contacts (ie the clearance between all sealing surfaces of the backward transfer region) and the presence of their local defects. This characteristic may be different for different transferred volumes. However, due to the local pressure balancing means as one manifold of the channel 18 of the vane 8, the channel 27 of the support part of the rotor and the channel 26 of the cannulated connector 12, its transferred volume The pressures of all the cavities 22, 18, 7, 14, 27 and 25 forming the same are the same.

Due to the above characteristics of the support cavities 25 of the support part 4 of the rotor and the sealing shoulders 67 of the support cover plate 5 of the housing of the force chambers 6, the support cavities 25 side And the pressure forces exerted on the support part 4 of the rotor from the force chambers 6 side of the backward transfer region D, except for the minimum necessary to press the support part of the rotor against the support cover plate of the housing. Balance each other.

The size of the bottom sealing ledge 23, the sealing shoulders 66 of the working cover plate of the housing and the force chambers 6 is the pressure force of the fluid applied to the working part of the rotor from the bottom unloading cavity 22 side. They are smaller than the pressure forces from the force chambers 6 side by a small value selected for minimally pressing the actuating part of the rotor against the actuating cover plate 3 of the housing. The mutual position of the bottom unloading cavities 22 and the force cavities 14 is chosen such that the back pressure forces of the working fluid acting on the actuating part of the rotor are minimized.

Thus, irrespective of the zone of the working chamber in which the vane is selected, the pressures of the supporting chamber and force chamber of the vane chamber and the support part of the rotor connected to the vane chamber, Equal to pressure.

The shape, size and position of the support cavities and the force cavities of the force chamber, taking into account the insulating means of the support cavities, are such that, at the same pressure, forces applied to each rotor part from the force chambers side from the corresponding cover plate side of the housing It is chosen to exceed the forces applied to it, the difference being the value required to compress the sealing surfaces of this part of the rotor against the sealing surfaces of the functional elements of the corresponding cover plates of the housing.

The power frictional loss of the face sealing parts is determined by the force value which compresses the parts of the rotor against the functional elements of the corresponding cover plate of the housing, which can be chosen small. For example, the occurrence of local defects on the sealing surfaces due to wear and contamination of the working fluid by suspended particles do not lead to an increase in the compressive force. The hydraulic resistance and maximum self suction speed of the channels that determine the pressure drop in the vane chamber can be selected according to the required rotor rotational operating speed.

Claims (24)

A housing (40) having an inlet port (49), an outlet port (50), an operating cover plate (3) and a support cover plate (5) having a forward transfer limiter (15) and a backward transfer limiter (21); It comprises one rotor comprising the actuating part 1 of the rotor with the vane chamber 7; The working face of the part (1) has an annular groove (2) connected to a vane chamber (7) comprising vanes (8) kinematically connected to a vane drive mechanism (54) mounted to the housing; The operating cover plate 3 of the housing, which is in sliding insulating contact with the operating face surface of the operating part 1 of the rotor, forms one working chamber in the annular groove 2, which annular recess transfer groove of the rotor. The working chamber 28 hydraulically connected to the inlet port 49 by means of a backward transfer limiter 21 in sliding insulation contact with the rating means and a forward transfer limiter 15 in sliding insulation contact with the vanes 8. The pumping cavity of the working chamber 51 hydraulically connected to the suction cavity of the suction cavity and the outlet port 50; The forward transfer limiter 15 and the vane drive mechanism 54 are made by the vane 8 so as to be able to separate at least one vane inner cavity 62 of the working chamber from the pumping and suction cavities; The rotor is also: The rotor parts comprise a force chamber 6 which is slidingly insulated in contact with the support cover plate 5 of the housing and is hydraulically connected to the actuating part 1 of the rotor by the rotor element assembly and has a variable length. Of the rotor, which can be moved and tilted axially with respect to the operating part 1 of the rotor at least sufficiently to make sliding insulation contact with the corresponding cover plate of the rotor and to rotate simultaneously with the operating part 1 of the rotor It comprises a part (4); Changing the length of the force chambers (6) of variable length causes the actuating part and support part of the rotor to move and tilt in the axial direction as described above; Between the support cover plate 5 of the housing and the support part 4 of the rotor, support cavities 25 with insulating means are made; Wherein the cavities of the working chamber are in hydraulic communication with at least one force chamber (6) and at least one support cavity (25) of variable length via local pressure force balancing means, respectively. The insulation of the cover plates according to claim 1, wherein the housing is made such that the actuation and support cover plates of the housing are joined to the actuation unit 38 of the housing located between the actuation part and the support part of the rotor. A rotor sliding-vane device, comprising hydrostatic means for preventing deformation of the rating surfaces. 3. The force according to claim 2, wherein the rotor comprises a rotor linking element 37, wherein at least one of the parts of the rotor is mounted so as to be able to axially move and tilt relative to the linking element, the force being variable in length A rotor sliding-vane device, wherein chambers (6) are located between the part of the rotor and the rotor linking element (37) to kinematically connect the part of the rotor to the linking element. 2. The apparatus of claim 1, wherein the housing comprises hydrostatic means for preventing deformation of the insulating surfaces of the cover plates; The hydrostatic means: functional element (30) in sliding insulating contact with a corresponding part of the rotor, at least one of the cover plates of the housing; Load bearing elements 29 of the cover plate; And at least one anti-deformation chamber 31 between the functional element and the load bearing element and hydraulically connected to the working chamber, wherein the functional element 30 of the cover plate is from the anti-deformation chamber 31 side and the rotor side. Rotor sliding-vane device, wherein the working fluid pressure forces exerted on) are made to remain generally balanced with each other. 5. Rotor sliding-vane device according to claim 1 or 4, wherein a local pressure balancing means is formed of one manifold of the hydraulic circuits of the rotor to provide the connection of the cavities. 4. A rotor according to claim 1, 2 or 3, wherein the local pressure balancing means is formed of one manifold of the hydraulic circuits of the rotor and one manifold of the hydraulic circuits 27-1 of the housing. Wherein the circuits each provide the connection of the cavities through at least one of the circuits of the housing irrespective of the rotor rotation angle. 7. The channel of the support part 4 of the rotor according to claim 5, wherein the manifold of the hydraulic circuits of the rotor connects the force chambers 6 of variable length to the support cavities 25. 27). Rotor sliding-vane device. 7. Rotor sliding-vane device according to claim 5 or 6, wherein the manifold of the hydraulic circuits of the rotor comprises vane chambers (7). 9. Rotor sliding-vane device according to claim 5, 6 or 8, wherein the manifold of the hydraulic circuits of the rotor comprises channels (18) of the vane (8). 7. The housing according to claim 6, wherein the manifold of the hydraulic circuits of the housing comprises channels 27-1 of the housing connecting the support cavities 25 to the annular groove 2 of the actuating part 1 of the rotor. Rotor sliding-vane device. 7. The hydraulic circuit of claim 5 or 6, wherein the circuits each have a hydraulic resistance selected such that the pressure drop therein is generally less than the nominal working pressure of the device at a working fluid flow rate less than the maximum leakage allowed from the working chamber. A rotor sliding-vane device, wherein the pressure drop is preferably less than 1% of the nominal operating pressure. The force chamber (6) according to any one of the preceding claims, wherein the variable length force chamber (6) is formed of container elements (11) and embedded elements (10) mounted so as to be able to move alternately, and the embedded element. The outer walls of the fields 10 are in sliding insulating contact with the inner walls of the container elements 11 to provide a sealing of the force chambers 6 when the parts of the rotor alternately move and tilt in the axial direction as described above. , Rotor sliding-vane device. 13. The supporting part of the rotor according to any one of the preceding claims, wherein working fluid pressure forces for pushing the operating part 1 of the rotor out of the operating cover plate 3 of the housing. (4) The shape, dimensions and position of the support cavities 25 and their insulation means are selected such that they are generally the same and opposite in direction to the actuating fluid pressure forces that push out, and the parts are removed from the corresponding cover plate of the housing. So that an excess of the pressure forces of the working fluid contained in the variable force chambers acting on the parts of the rotor above the pushing out working fluid pressure forces of the rotor is at least sufficient to provide the squeezing required for insulation; Preferably, the shape, dimension and top of the force chambers 6 of varying lengths to provide a small compression regardless of the rotor rotation angle. Rotor sliding, is selected - the vane apparatus. 13. The supporting part of the rotor according to any one of the preceding claims, wherein working fluid pressure forces for pushing the operating part 1 of the rotor out of the operating cover plate 3 of the housing. (4) the shape, dimensions and position of the support cavities 25 and their insulating means are selected such that they are generally the same and opposite in direction to the working fluid pressure forces that push out; Wherein the assembly of rotor elements comprises elastic elements 59, which provide the compression necessary for insulation at a no pressure against the corresponding cover plate of the housing of the parts of the rotor, Working force pressure forces pushing the parts of the rotor out of the corresponding cover plate of the housing and the force chambers 6 of variable length, which act on the parts of the rotor above a sum of the frictional forces of the assembly of the rotor elements. Preferably, a small compression is provided so that an excess of the sum of the pressure forces of the working fluid contained therein and the elastic forces of the elastic elements 59 is at least sufficient to provide the compression necessary for insulation at least. The rotor sliding-vane device is selected so that the shape, dimension and position of the force chambers (6) of varying length are selected. 15. The cross-sectional area of all force chambers 6, according to claim 13 or 14, which is variable in length with respect to the area of the projection of the annular groove 2 in the plane perpendicular to the axis of rotation of the actuating part 1 of the rotor. The shape and dimensions of the force chambers 6 which are variable in length, such that the excess of these sums is at least 50% of the area of the sliding insulating contact of the operating part 1 of the rotor with the operating cover plate 3 of the housing. The rotor sliding-vane device is selected. 15. The method according to claim 13 or 14, wherein the support cavities 25 are located opposite the annular groove 2, and the insulating means of the support cavities are arranged around the insulating dams 57 between the support cavities 25. Face seals 58; The sum of the areas of the support cavities 25 and the insulating dams 57 is equal to the area of the annular groove 2 projection with respect to the plane perpendicular to the axis of rotation of the actuating part 1 of the rotor; The area of the sliding insulating contacts of the peripheral face seals 58 with the insulating surfaces of the support cover plate 5 of the housing is the sliding of the operating cover plate 3 of the housing and the operating part 1 of the rotor. Rotor sliding-vane device, such as a corresponding area of insulating contacts. 18. The rotor according to claim 16, wherein the backward transfer insulating means of the rotor is connected with at least one of two adjacent vane chambers (7) by bottom sealing ledges (23) in sliding insulating contact with the backward transfer limiter (21). It includes portions of the surface of the annular groove bottom 20 between the vanes 8, including separate bottom unloading cavities 22, with insulating dams 57 opposite the bottom sealing ridges 23. A rotor sliding-vane device, wherein the area of the sliding contact surfaces of the insulating dams 57 is equal to the area of the sliding surfaces of the bottom sealing ledges 23. 5. A rotor according to claim 4, wherein the rotor is located between the operating cover plate and the support cover plate of the housing connected by the housing linking element 33, Support cavities 25 are made (4) on the support part of the rotor, The local pressure balancing means comprise channels 27 of the support part 4 of the rotor connecting the support cavities 25 to the vane chamber 7 and to the force chambers 6 of variable length, and , The support cover plate 5 of the housing is hydraulically connected to the inlet port 49 and has at least one suction dispensing cavity 28-1 opposite the suction cavity 28 of the working chamber so that the support part of the rotor ( A rotor sliding-vane device, in communication with the support cavities 25 of 4). 19. The at least one pumping dispensing cavity (51-1) according to claim 18, wherein the support cover plate (5) of the housing is hydraulically connected to the outlet port (50) and located opposite the pumping cavity of the working chamber (51). Rotor connected to the support cavities (25) of the support part (4) of the rotor. The surface of the support cover plate of claim 1, wherein the surface of the support cover plate of the housing in sliding contact with the support part of the rotor, the forward transfer limiter 15 facing the operating cover plate of the housing and the backward transfer limiter 21 is supported. Having a forward transfer limiter 15 and a backward transfer limiter 21 of the cover plate, The face of the support part of the rotor in sliding contact with the support cover plate of the housing has an annular groove 2 connected to the vane chambers 7 of the support part of the rotor, The support cavity insulation means comprises vanes 8 located in the vane chambers 7 and kinematically connected to the vane drive mechanism 54 so that they slide with the forward transfer limiter 21 of the support cover plate of the housing. Rotor sliding-vane device in insulating contact. 21. The rotor sliding vane device according to claim 20, wherein the support cavity insulation means comprises portions of the bottom of the annular groove between the vanes in sliding insulation contact with the backward transfer limiter 21 of the support cover plate of the housing. . 21. The support cavity insulator according to claim 20, wherein the support cavity insulating means is located in the vane chambers 7 of the support part of the rotor and kinematically connected to the vane drive mechanism 54 such that the vanes are mounted on the back of the support cover plate of the housing. A rotor sliding-vane device comprising vanes (8) in sliding insulating contact with a word transfer limiter (21). 2. Rotor sliding-vane device according to claim 1, wherein the backward transfer insulation means of the rotor comprises portions of the annular groove bottom (20) surface between vanes (8). 24. The bottom sealing ledges (23) according to claim 21 or 23, wherein said parts of the annular groove bottom (20) are in bottom sealing ridges (22) in which a bottom unloading cavity (22) is in sliding insulating contact with said backward transfer limiter (21). A rotor sliding-vane device, having bottom unloading cavities (22) separated by at least one of two adjacent vane chambers (7).

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