JP2009508039A - Method for generating an undulating flow of working fluid and apparatus for the method - Google Patents

Abstract

  Rotation of the rotor (2) of the rotor sliding blade device, separation of the fluid in the transport hole (9) from the inlet hole (6) by the blade (4), and the outlet hole (7) of the device in the transport hole And the volume of the transport holes and their fluid pressures change during the transport process, and the pressure is changed according to the moment when the transport holes are merged with the exit holes. A method of generating a fluid flow that is less undulated by a confluence followed by fluid movement characterized by being made substantially equal to the outlet pressure. A rotor sliding blade device having an annular groove working chamber on the surface of the rotor comprises a blade chamber and a blade of a variable capacity forced chamber (10). The apparatus comprises means for changing the capacity of the forced chambers and their fluid pressure, and means for adjusting the degree of pressure change of the working fluid in the forced chamber.

Description

  The present invention relates to mechanical engineering and can be used in rotor sliding vane pumps and hydraulic motors operating at high pressures to substantially reduce the flow of working fluid flow and the level of vibration and noise generated thereby. .

  There is known a method for generating a non-rippling flow of working fluid using a rotor sliding blade device configured as follows. The structure is such that a blade sliding with the rotation of the rotor along the inner surface of the housing separates the conveying portion of the working fluid in the conveying hole from the inlet hole of the housing of the inlet pressure device, and the conveying hole is merged with the outlet hole. , After the transfer portion is replaced by the outlet hole, the transfer portion of the working fluid is transferred to the outlet hole of the housing of the device having an outlet pressure that is not substantially equal to the inlet pressure.

  The method for generating an undulating flow of working fluid includes two variations of hydrodynamic deformation of power in the rotor sliding blade device. In the first variant, mechanical power is supplied to a rotating shaft that generates a rotating flow of working fluid from a low pressure inlet hole to a high pressure outlet hole. In this case, the rotor device operates as a pump and converts mechanical power into hydraulic power.

  In the second variant, the high-pressure working fluid is conveyed into the inlet hole of the rotor sliding blade device and rotates the rotor, thereby converting hydraulic power into mechanical power. In this case, the device operates as a hydraulic motor.

  In the following, a method of generating a non-rippling flow of working fluid that converts mechanical power into hydraulic power as a basic modification will be described. That is, a rotor sliding vane device as a pump that remembers that all the effects do not change due to different hydraulic forces due to the opposite signal of the pressure drop between the inlet and outlet holes. Because of the rotor device that operates as a pump, the inlet holes are called suction holes, outlet holes, and pumping holes. The conveyance area of the conveyance part from the inlet hole to the outlet hole is called a front conveyance area.

  Current rotor sliding blade devices implementing this method are subdivided into two main types depending on the configuration of the working chamber.

  In a first type of rotor device, the working chamber is wound by a cylindrical surface inside the housing and a cylindrical surface outside the rotor. The blades of such devices are usually arranged with the possibility of moving radially with respect to the rotor (Pump Handbook, Igor J. Karasik, Joseph P. Mesina, Paul Cooper, Charles Sea. Heald, McGraw-Hill Copyright 2001, 1986, 1976, section 3.8). The housing and rotor surface that form the working chamber in such a device have different curvatures. Therefore, the flow uniformity, i.e. the constant speed of suction and pumping, can be supplied at their constant position only relative to each other. The movement adjustment by changing the distance between the rotor and the cylindrical surface of the housing is kinematically conveyed. In the following, movement means the volume of working fluid carried by the rotor device from the inlet duct to the outlet duct with one rotation of the rotor.

  In a second type of rotor device, the working chamber is wound by the surface of the rotor and the inner surface of the cover plate of the housing arranged oppositely. This type of device is relative to the rotor, such as axial movement (U.S. Pat. No. 5,570,584), radial movement (U.S. Pat. No. 8,894,391), and blade rotation (U.S. Pat. No. 10,968,804 and U.S. Pat. No. 2,341,710). Supply different moving types of blades. For any type of blade movement, in the following, the hole in which the blade is placed is referred to as the blade chamber. The flat surface of the housing that forms the rotor and the working chamber provides a constant transport at any distance between them, i.e. any movement.

  The arrangement of the annular groove working chamber on the rotor surface of the pump (US Pat. No. 1,109,804, US Pat. No. 3,315,164, US Pat. No. 6,547,546 and Russian Patent No. 2,157,731) is the radial unloading of the rotor in the working chamber. And provide firm fixation of the blades. The main sealing between the mutually rotating parts of such a pump is that the annular groove is made and the surface of that part of the rotor, referred to below as the working part of the rotor, and the housing cover adjacent to said annular groove It is moved to the corresponding surface of the plate, hereinafter referred to as the working cover plate of the housing. The sealing surfaces of the rotor and the housing can be formed flat. Therefore, other gaps between the technical thermal flat sealing surfaces are facilitated by the forward movement of one sealing surface relative to the other due to the pressing of the working part of the rotor against the working cover plate of the housing. To be taken.

  In most known rotor sliding blade devices, the fluid portion is returned from the outlet hole to the inlet hole at the rotor hole and the hole formed between the rotor and the housing. In the following, these holes are referred to as rear transport holes, and the portion of the working fluid contained in them is the rear transport portion. The conveyance area of the rear conveyance part of the working fluid contained in the rear conveyance hole from the outlet hole to the inlet hole is hereinafter referred to as a rear conveyance area.

  Consider the device described in Russian Patent No. 2,175,731, which is most similar to the device performing the method described above.

  The above-mentioned patent describes a pump having a housing with an actuating cover plate and a support cover plate, referred to in the patent as a “housing cover plate”. The face of the rotor located opposite the working cover plate of the housing has a cylindrical shape that passes through a vane chamber called the "rotor opening" in the patent with vanes called the "displacer" in the patent An annular groove is provided. The surface of the rotor is arranged on the opposite side of the annular groove and contacts it with the possibility of sliding along the face of the sealing element, and placed on the opposite side of it, the slot in the working cover plate of the housing Is attached. The pump has a rear transfer limiter that separates the suction hole from the pumping hole, which the patent calls a “partition”. The suction holes connected to the inlet holes are called “inlet openings” in the patent, and the pumping holes connected to the outlet holes are called “outlet openings” in the patent. The surface of the rear conveyance limiter that is in sliding contact with the rotor means for blocking the rear conveyance is called “the inner surface of a cylindrical annular groove” in the patent. The rear transfer limiter is fixed to the operating cover plate of the housing. The pump includes a blade drive mechanism that the patent calls a “mechanism for setting the axial arrangement of displacers relative to each other”. The element of the housing that is in sliding insulation contact with the vanes is such that the distance between it and the rotor determines the movement of the device, and is referred to in the following as a forward transport limiter. The pump forward limiter is formed by a portion of the inner surface of the working cover plate. In an adjustable embodiment of the device, the patent refers to the forward transport limiter as an “insulating element movable in the axial direction”. The second surface of the rotor contacts the support cover plate of the housing.

  The method and the rotor apparatus in which it is implemented have the major disadvantage that the flow waves due to a considerable pressure drop between the inlet and the outlet. It is caused by the fact that fluid flows from the suction hole to the transport hole at the inlet pressure. Thereafter, the transport portion is transported to the closed transport hole. In the device with the working chamber made in the annular groove described above, the transport hole is formed by the inner part of the annular groove between two adjacent blades and the hole inside the rotor connected to the working chamber, for example the blade chamber. It is formed. When the insulating means removes internal leakage of the working fluid between the pressure feed hole and the suction hole via the front transfer region, the pressure of the transfer portion of the fluid being transferred does not reach the outlet pressure thereafter.

  As a result, when the transport hole merges with the pressure feed hole, there is a large difference between the pressure at the fluid transport portion and the fluid pressure at the pressure feed hole. Due to the compressibility of the working fluid, the opposite flow of fluid depressurization from the suction hole to the transfer hole appears periodically, balancing the pressure, causing the flow rate of the pumping area and pressure system and the periodic wave of pressure. The overall magnitude of the reduced pressure of the fluid transport carried to the transport hole by such pressure reduction depends on the pressure difference balanced with the compressibility of the fluid.

Since different working fluids have different constant compression ratios, the pressure drop values at which the above depressurization effects begin to appear are different. For ordinary industrial oils having a compressibility factor of about 0.001 MPa ⁻¹ , the above-described depressurization effect begins to appear with a pressure drop of several MPa.

  With an outlet pressure of several tens of MPa, the overall size of the vacuum transfer reaches several percent of the size of the fluid transfer part. With a considerable capacity of the rear transfer part of the working fluid transferred from the pumping area to the suction area, the corresponding pressure wave in the pump suction system caused in this case by the expansion of the reduced pressure of the fluid from the rear transfer hole to the inlet hole Sometimes it happens. The wave frequency is determined by the frequency of origin of the reduced pressure flow. The level of decompression wave depends on many factors such as pressure drop, insulation quality, rotor rotation speed, the ratio of the hole capacity to the transport capacity under the outlet pressure and their hydrodynamic properties.

  In practical moving pumps with good pumping pressure and good insulation means, these waves are the main reason for causing noise and vibration in hydraulic systems that often eliminate hydraulic drive for electric drive A certain value of can be reached.

  Such a result of the effect is also described as a decrease in overall hydrodynamic efficiency at high pumping pressure. In fact, the displacer consumes an additional part of the power supplied to the drive of the pump to replace the overall size of the vacuum transport carried from the pumping hole back to the pumping hole by the opposite vacuum flow to the transport hole. Let the additional work you do. This additional power is not transferred to the pumping system when it is converted by the vacuum flow opposite to the heating of the working fluid, hydraulic system vibrations, pumping and suction duct sound waves, and audible noise.

  As the volumetric efficiency of the pump increases due to the improved quality of the sealing element, the power loss due to leakage of the tea ceremony fluid decreases, the power of the decompression flow increases, and at the pump maximum pipe and pumping pressure of several tens of MPa it is Reaching a few percent of the power delivered to the. In the majority of variable displacement pumps, the transfer to the pressure system is reduced by a simultaneous decrease in the capacity of the transfer part and an increase in the capacity of the rear transfer part. It is clear that the power loss due to such pump depressurization exceeds the useful power delivered to the load at high pumping pressure and low delivery to the load.

  For example, the application of passive means to smooth over the pressure wave of reduced pressure, such as the throttle tube on the surface of the forward transfer limiter (patent EB00374731), reduces the magnitude of the pressure wave that increases their duration. , Thereby reducing the burden of hydraulic system noise and vibration power loss, which increases the loss by heating the fluid. However, the overall level of power loss due to decompression cannot be reduced by such passive means.

  At a high rotational speed of the rotor, the pressure reduction impact caused by joining the volumes conveyed to the pumping area has a steep front edge. As a result, high-frequency acoustic waves are generated in the pressure system. The capacity of the pressure system in this case can be considered as a distribution characteristic, and a mere increase in this capacity does not always lead to a corresponding decrease in decompression waves and the associated high frequency components of noise and vibration.

  The object of the present invention is to reduce the wave level of the working fluid flow caused by the decompression of the rotor sliding blade device and thereby reduce the power loss due to the generation of noise and vibration and the heating of the working fluid in the hydraulic system It is to let you.

  The present invention achieves this object by the following method. That is, the non-fluid flow of the working fluid is generated by the rotation of the rotor of the rotor sliding blade device, filling the inlet hole of the device with fluid at the inlet pressure, and at the outlet pressure not substantially equal to the rotor and inlet pressure. The conveying hole between the blades separated from the outlet hole of the apparatus is connected to the inlet hole of the rotor, the conveying part of the working fluid is separated from the inlet hole of the conveying hole by the blade, the conveying hole is connected to the outlet hole, This is a method of moving the working fluid to the outlet hole of the apparatus. Each transport hole corresponds to its respective range of rotor rotation angles at which the transport hole is separated from the inlet and outlet holes. During the movement of the transfer hole, the pressure of the transfer portion of the working fluid changes due to the change of the transfer hole capacity, and the pressure becomes substantially equal to the outlet pressure at the moment of confluence of the transfer hole and the outlet hole. It has become.

  In a rotor sliding blade device that operates as a pump, the pressure in the outlet hole, also called a pressure feed hole, exceeds the pressure in the inlet hole, also called a suction hole. Therefore, the present invention reduces the capacity of the transport hole of the pump and correspondingly increases the pressure of the transport part during movement from the suction hole to the pumping hole of the pump. In a device operating as a hydraulic motor, the pressure in the outlet hole is lower than the pressure in the inlet hole. Therefore, the present invention increases the capacity of the transport hole of the hydraulic motor and correspondingly decreases the pressure of the transport part during their movement from the inlet hole to the outlet hole of the hydraulic motor. In the following, a method of generating a non-wave-like flow of working fluid in a rotor sliding blade device that operates as a pump as a basic modification will be described. The described solution is also applicable to hydraulic motors that are modified according to the opposite signal of the pressure drop between the inlet and outlet holes.

  The change in the working fluid pressure in the conveying portion due to the change in the capacity of the conveying hole so that the pressure described above becomes substantially equal to the outlet pressure at the moment when the conveying hole merges with the outlet hole is the same as the conveying hole at the moment of merging described above. Remove the origin of the reduced pressure flow between the outlet holes. Thereby, the waves generated by these decompressed flows are eliminated, and the non-uniformity of the working fluid flow is improved.

  In order to carry out the method of generating an undulating flow of working fluid, the apparatus is provided with a housing having an inlet hole and an outlet hole, and comprises a working cover plate having a forward conveying limiter and a rear conveying limiter formed thereon. . The apparatus comprises a rotor chamber having a vane chamber of an actuating portion and a vane chamber having vanes kinematically connected to a vane drive mechanism formed on the surface of the actuating surface of the actuating portion of the rotor and attached to the housing. And an annular groove connected to the. The working cover plate of the housing is in sliding insulating contact with the surface of the working surface of the working part of the rotor, forming an annular groove working chamber. Similar to the forward conveying insulated rotor means in sliding insulation contact with the forward conveying limiter, the rear conveying insulating rotor means in sliding insulation contact with the rear conveying limiter are provided with vanes and separated from each other, and the inlet hole is hydraulically connected to the inlet. Connected, the outlet hole is hydraulically connected to the outlet, and the at least one transport hole includes an annular groove, a forward transport limiter, and an inner blade hole joined by the surfaces of two adjacent blades. Each transport hole corresponds to its respective range of rotor rotation angles where the transport holes described above are separated from the inlet and outlet holes.

  In order to reduce the wave level of the working fluid flow, each transport hole comprises at least one forced chamber connected to the hole of the inner vane contained in the transport hole described above, and each forced chamber is connected to the inlet hole. With the possibility of changing the balance between the capacity of the forced chamber at the rotation angle of the rotor and the capacity of the same forced chamber at another rotation angle of the rotor to which it is connected to the outlet hole Kinematically connected to the capacity changing means.

  The essence of the provided invention is illustrated by means of a diagram and a drawing of an apparatus implementing the above method.

FIG. 1 shows (a) the dependency relationship of the capacity of the transport hole due to its angular movement, and (b) the inlet hole _φdeatch. From the separation angle of the conveying hole from the outlet hole φ _merg. FIG. 2 shows two types of graphs showing the dependency of the pressure of the conveying portion of the working fluid in the conveying hole by the angular movement φ within the range of the rotation angle _φtotal of the rotor to the angle at which it is merged. Hereinafter, the angle and the corresponding angular movement are understood as the rotation angle of the rotor about its axis of rotation. The chart is given for different types of transport hole capacity dependency due to its angular movement. That is, when the transport hole has a constant capacity (curves 1a and 1b), when the capacity of the transport hole given to make the pressure equal to the outlet pressure is decreased (curves 2a and 2b), and when it is insufficient (curve) 2a, 2b) and a case where the capacity of the transport hole is excessively reduced (curves 4a, 4b). All charts are given for an ideal pump, ie a device that operates as a pump where there is no change in the size of the conveying part due to leakage.

  The diagram of FIG. 2 shows the time-based outlet pressure with reduced pressure waves for different degrees to reduce the capacity of the transport hole. All charts are given for the same equipment and the same conditions as in FIG. The curves in the chart are a curve 5 that is a constant capacity of the transport hole, a curve 6 that is a change in the capacity of the transport hole that equalizes the pressure, a curve 7 that is an insufficient change in the capacity of the transport hole, and a curve 7 It corresponds to curve 8 which is an excessive change in capacity.

  FIG. 3 shows a housing 1 with a rotor having a blade chamber formed in the working part 2 of the rotor and with a blade in sliding insulation contact with a forward conveying limiter 5 formed in the housing and exiting from an inlet hole 6 The change of the capacity | capacitance of the conveyance hole of the rotor sliding blade apparatus which isolate | separates the internal blade hole 8 in the hole 7 is represented. Each transport hole 9 includes an inner vane hole 8 and a forced chamber 10 connected to the rotor and formed in a rotor similar to a hydraulic cylinder, and the capacity of the transport hole 9 is the capacity of the forced chamber 10 by the rotation of the rotor. Realized by periodic changes in capacitance. The periodic change in the capacity of the forced chamber 10 can be realized, for example, by a kinematic connection of the movable wall 11 of the forced chamber 10 having a cam mechanism 12 attached to the housing 1. The preferred embodiment (FIG. 4) has a support part for the rotor 13 which is mounted with the possibility of rotating simultaneously with the working part of the rotor 2 and is inclined with respect to the support part 13 of the rotor. The mutual inclination of the rotating shaft of the operating part 2 causes a periodic change of the capacity of the forced chamber 10 by the rotation of the rotor.

  Changing the capacity of the transfer hole by changing the capacity of the forced chamber as the rotation of the rotor changes the extent of blade sliding along the forward transfer limiter and separates this transfer hole from the rotor inlet and outlet holes. It can be replenished by changing the capacity of the inner blade hole.

  The reduction in the volume of the closed transport hole of the pump to achieve the pressure is equal to the pumping pressure required to do the compression work of the working fluid and therefore requires a constant power consumption. This power consumed for compressing the fluid is transferred to a pressure system that is larger or smaller than the ratio of the capacity of the transport hole and the capacity of the rear transport hole, and can be used for the load by expansion of the compressed fluid. The proportions described above depend on the structure of the pump, and for variable displacement pumps it also depends on the current movement of the pump. The other part of the power consumed for compression is proportional to the proportion of working fluid returned from the outlet hole to the inlet hole through the rear conveying region and back to the rear conveying hole. The preferred embodiment of the present invention provides such a change in the capacity of the rear transport hole such that the moment of merging of the rear transport hole and the inlet hole causes their pressure to be substantially equal to the inlet pressure. In the mode of the pump where the outlet pressure exceeds the inlet pressure, the rear conveying hole closed in the rear conveying area is increased by supplying a decrease in the working fluid pressure to the inlet pressure value. In this case, the working fluid confined in the closed rear transfer hole expands work. This other part of the power consumed to compress the working fluid returns to driving the pump. In the hydraulic motor mode, the increase in the capacity of the transport hole in the movement from the inlet to the outlet hole causes the working fluid compressed by the expansion to save the recovery potential power.

Adjusting the range of pressure change in the working fluid conveying part At a predetermined mixing and constant temperature of the working fluid, the pressure Pi (φ) of the working fluid conveying part is equal to the capacity Vi (φ) of the conveying hole and the conveying part of the working fluid. It is determined by the mass Mi (φ). At the moment of separation of the transport hole from the inlet hole, its volume Vi ( _φdeatch.i ) and its working fluid mass Vi ( _φdeatch.i ) are determined by movement of the device. Inlet hole _{φdetach of the} transfer hole _. From the separation angle from i, outlet hole φ _merg. The rotation angle φ _total of the rotor to the merging angle with i _. The change in the mass Mi (φ) of the working fluid in the conveying hole at that angular movement within the aforementioned range of i is a flow rate ratio DRi (φ) to the i conveying hole due to leakage from it and inflow into it from the high pressure hole This is the movement of the working fluid. In the predetermined characteristic of the insulating means of the rotor sliding blade device, the change in the mass dMi (φ) of the sailing portion of the working fluid depends on the difference dP between the outlet pressure and the inlet pressure, and the rotational speed ω of the rotor. In the movement of the transport hole from the inlet hole to the outlet hole, its capacity Vi (φ) changes according to the selected dependency of the variable part of the capacity of the transport hole Ai (φ) of its angular movement.
Vi (φ) = Vi ( _φdeatch. I) + Ai (φ)
From the viewpoint of the present invention, an important characteristic of the dependency relationship Ai (φ) is a change range of the capacity of the transport hole in a predetermined angle range φ _total i, which will be referred to as an overall size of the change of the capacity of the transport hole in the following.

_{A total = Ai (φ merg.} I) -Ai (φ detach. I) = Vi (φ merg. I) -Vi (φ detach. I)
In order to achieve the transport hole pressure Pi (φ _merg. I) by the moment of merging with the outlet hole equal to the outlet pressure P _out , the rotor moves with the movement of the device due to the difference dP between the outlet pressure and the inlet pressure. The change in the rotation speed ω and the mass of the working fluid in the conveying hole provide adjustment of the range of pressure change in the conveying portion of the working fluid resulting from the change in the capacity of the conveying hole. The present invention provides two methods of such adjustment.

The first method is preferred in terms of the level of flow non-uniformity caused by a large change in the difference between the inlet pressure and the outlet pressure, and the overall change in the capacity of the transport hole in a predetermined angular range φ _total i. It is provided that the adjustment is performed by changing the magnitude Atotal and changing the dependency Ai (φ). This method will be referred to as an overall size adjustment method in the following.

A second method suitable in terms of cost is a predetermined dependency Ai (φ), and the transport hole is _φmerg. by changing i or _{φdeatch. φdetach} separated from the inlet and outlet holes by changing i _. i to φ _merg. The adjustment is executed by changing the range of rotation angle φ _total i of the rotor to i. This method is hereinafter referred to as the overall angle adjustment method.

  Both adjustment methods are considered in detail below.

The present invention is a method of adjusting the size of the transfer hole by changing the inlet pressure and the outlet pressure dP and the change in the mass of the working fluid in the transfer hole dM. The overall size Atotal changes.

  When the movement of the device increases, the overall size Atotal also increases. If the movement of the device is reduced, the overall size can be changed, for example, with the possibility of changing the angle of inclination of the axis of rotation relative to the axis of rotation of the working part of the rotor, or separate of the movable walls of the force chamber. This is reduced by the kinematic connection between the forward transport limiter and the support part of the rotor formed by the drive mechanism. When the magnitude of the difference dP between the outlet pressure and the inlet pressure increases, the overall magnitude Atotal also increases, and when the difference decreases, the magnitude also decreases. The curve 9a in FIG. 5 describing the change in the capacity Vi of the transport hole and 9b describing the change in its pressure Pi correspond to a larger pressure drop dP, and the curves 10a and 10b correspond to a smaller pressure drop dP. The adjustment of Atotal depending on dP can be performed using, for example, a pressure sensor and an electric drive.

In order to make the transport hole pressure Pi more precisely equal to the outlet pressure Pout, in particular, at a variable speed of rotation of the rotor, or at a variable temperature and viscosity of the working fluid, the present invention provides a combination of the inlet pressure Pin and the outlet pressure Pout. Between a reference pressure P _ref (Pin, Pout) equal to a selected value between and a pressure P i (φ _ref i) of the conveying hole at a selected rotation angle of the rotor equal to the reference angle φ _ref i The overall size Atotal is adjusted by the difference. The reference angle φ _ref i is the separation angle φ _detect. i from merging angle φ _merg. i is selected within i, i.e., φ _ref i is selected equal to the angle shifted by the selected shift angle φ _shift relative to the angle at which the i transport hole meets the exit hole. That is,
φ _ref i = φ _merg. i-φ _shift
A person skilled in the art will determine that this hole has a predetermined leakage rate through the predetermined dependency of the capacity of the conveying hole of the rotor rotation angle Vi (φ) and the insulating means of the selected conveying hole at a predetermined rotational speed of the rotor. The pressure Pi (φ _ref i) of the transfer hole at the rotation angle of the rotor equal to the reference angle φ _ref i and the pressure Pi (φ _merg.) At the rotation angle of the rotor where the transfer hole merges with the outlet hole _. It can be seen that there is a specific correspondence with i).

Therefore, in the pump mode at a predetermined outlet pressure Pout, the value of the reference pressure P _ref (Pout) is set under the condition that the pressure Pi and the outlet pressure Pout of the conveying portion are equalized at the moment when the conveying hole joins the outlet hole. It is determined. At the reference angle, if the pressure Pi (φ _ref i) of the transport hole of the pump is equal to or lower than the reference pressure P _ref (Pout), then the overall magnitude Atotal of the change in the capacity of the transport hole increases. Above the pressure, the overall size decreases. In a hydraulic motor, instead of the outlet pressure Pout, the inlet pressure Pin is used in the same way as the inverse relationship of the overall magnitude Atotal of the correlation between P _ref (Pout) and Pi (φ _ref i), ie the reference If the pressure of the transport hole of the hydraulic motor Pi (φ _ref i) is less than or equal to the reference pressure P _ref (Pin) at an angle, then the overall magnitude Atotal of the change in the capacity of the transport hole decreases, which is the reference When the pressure is exceeded, the magnitude increases.

Due to the difference between the reference pressure P _ref (Pout) and the pressure of the conveying hole at the reference angle Pi (φ _ref i), the overall magnitude Atotal can be adjusted using, for example, a pressure sensor and an electric drive It is. In a preferred embodiment of the invention, a hydraulic actuator is used, for example a differential double-acting hydraulic cylinder. In this case (FIG. 6), the overall size Atotal is adjusted by moving the piston 14 of the differential double-acting hydraulic cylinder 15. The piston 14 looks into the first hole 16 of the hydraulic cylinder 15 in the first direction. The pressure is below the reference pressure from the side, and the outlet pressure is below the second side looking into the second hole 17 of the hydraulic cylinder 15 (for the hydraulic motor below the inlet pressure). The hydraulic connection between the first hole 16 of the hydraulic cylinder 15 and the transport hole 9 is made with the opening angle φ _{unlock. Is} provided by opening the control valve 18 at a rotor rotation angle equal to the reference angle φ _ref and opening the control valve 18 at a rotor rotation angle equal to the reference angle φ _ref . When the first hole of the hydraulic cylinder 15 is connected to the transport hole 9 via the valve 19, if there is a difference between the reference pressure and the pressure of the transport hole, between the hole 16, the transport hole 9 and the piston 14. The flow of the working fluid moves. The deformation of the movement of the piston 14 to a change in the overall size Atotal is movable to the support part of the rotor formed with the possibility of changing the tilt angle of the axis of rotation or to the force chamber This is realized by the kinematic connection of the piston 14 to another drive mechanism on the wall.

  The ratio of the outlet (inlet for hydraulic motor) pressure to the reference pressure that makes the pressure of the conveying part equal to the outlet pressure at the moment when the conveying hole merges with the outlet hole is the ratio of the region on the first and second sides of the piston 14 and For example, it is determined by the value of the external force acting on the piston 14 from the side of the means for inclining the support portion of the rotor.

When the pressure in the transport hole of the pump at the reference angle Pi (φ _ref i) is equal to or lower than the reference pressure P _ref (Pout), the fluid flows from the first hole 16 of the hydraulic cylinder 15 to the transport hole 9, and the piston 14 Moving from the side to the first side, the overall magnitude Atotal of the change in the capacity of the transport hole is increased. When the pressure in the transport hole of the pump at the reference angle Pi (φ _ref i) exceeds the reference pressure P _ref (Pout), the fluid flows from the transport hole 9 to the first hole 16 of the hydraulic cylinder 15 and the piston 14 Moving from the first side to the second side, the overall magnitude of the change in the capacity of the transport hole is reduced. The pressure uniformity corresponds to the balance point of the piston 14.

The flow of fluid between the first hole of the hydraulic cylinder 15 and the conveying hole 9, referred to below as a compensatory comparative flow, changes the mass of the working fluid in the conveying hole at the same time as changing the overall size Atotal. And change their pressure. For insufficient pressure in the transport hole, Pi (φ _ref ) <P _ref (Pout), a compensatory comparative flow flows from the first hole of the hydraulic cylinder to the transport hole (curve 11a in FIG. 7) and the mass of the working fluid. And the pressure in the transport hole is increased (curves 11b and 11d). At excessive pressure in the transport hole, Pi (φ _ref )> P _ref (Pout), a compensatory comparative flow flows from the transport hole to the first hole of the hydraulic cylinder (curve 12a), the working fluid mass and the transport hole Is reduced (curves 12b and 12d). The types of the curves 13a to 13d indicate the operation of the transport hole in the stable operation mode of P _out 0.

With the rapid change in outlet pressure from P _out 0 to P _out 1, the change in the mass of the working fluid in the transfer hole due to the compensatory comparative flow can compensate for the inactivity of the overall size adjustment, This is considered to be a further advantage of such an adjustment method. The transition from the curve 13c in FIG. 7 to the curve 11c or 12c is due to the transfer by a compensatory comparative flow (curve 11a or 12a) of the portion of the working fluid from the first hole 16 of the hydraulic cylinder 15 to the transfer hole 9 because A total change is shown correspondingly. The curve 11c shifted after one transfer of mass from the first hole of the hydraulic cylinder is above the curve 14c, ie the overall size A ′ _total 1 can reach the value of the overall size A _total 1. Rather, it corresponds to the equilibrium position of the piston 14 at the pressure P _out 1. A curve 11b shows a change dMi of the mass of the transport hole when Pi (φ _ref ) <P _ref (P _out 0). Due to the increased mass, the change in the pressure of the transport hole Pi (φ _ref ) does not follow the curves 11 to 1d corresponding to an insufficient overall size A ′ _total 1 at a constant mass of the transport part, but the equilibrium In accordance with a curve 11d that more closely approximates the curve 14d corresponding to the overall size A _total 1, the pressure of the transport hole Pi (φ _ref ) is more balanced with the outlet pressure P _out 1 at the moment of merging. Similarly, the curve 12c is below the curve 15c, that is, the total size A ′ _total 2 after one mass transfer from the transfer hole to the hydraulic cylinder is the equilibrium position of the piston 14 at the pressure P _out 2 Corresponding to the total value A _total 2 does not reach. However, because of the smaller mass (curve 12b), the change in pressure in the transport hole Pi (φ _ref ) follows the curve 12d approximated by the curve 15d, so that at the moment of merging, the pressure in the transport hole Pi (φ _ref ) balance better with the pressure _{P out} 2.

In order to more accurately balance the transport hole pressure Pi with the outlet pressure Pout, the present invention provides an adjustment of the overall magnitude A _total of the change in capacity of the transport hole according to the magnitude and phase of the wave of the outlet pressure. In the mode of the pump where the outlet pressure exceeds the inlet pressure, it is done as follows. If the moment of joining the conveying hole to the outlet hole coincides with the positive rising front of the pressure wave (curve 8 in FIG. 2), A _total decreases, but the moment is the negative falling front of the pressure wave. If it matches (curves 5, 7), A _total increases. In the hydraulic motor mode in which the outlet pressure is equal to or lower than the inlet pressure, A _total increases, on the contrary, at the positive rising front at the instant and decreases at the negative falling front. When the magnitude of the outlet pressure wave increases, the rate of change of the overall magnitude increases.

Adjustment of the overall magnitude A _total by the magnitude and phase of the wave of the outlet pressure can be performed using, for example, a pressure wave sensor, a phase detector and an electric drive.

  The preferred embodiment of the present invention provides for the use of the method of adjusting the overall magnitude due to the difference between the reference pressure and the pressure of the conveying hole at the reference angle, where the reference angle is the magnitude of the wave of the outlet pressure. It depends on the height and phase.

  In the pump mode, if the outlet pressure exceeds the inlet pressure and the moment when the conveying hole merges with the outlet hole coincides with the positive rising front of the pressure wave, which shows an excessive value of the overall size, the value of the shift angle , Thereby bringing the reference angle closer to the angle at which this hole meets the outlet hole. Thereby, the pressure of the transport hole at the reference angle becomes higher than the reference pressure, and the overall size is reduced. When the moment coincides with the negative falling front of the pressure wave, the value of the shift angle increases, bringing the reference angle closer to the separation angle of the transfer hole from the inlet hole, and as a result, the pressure of the transfer hole at the reference angle is Below the reference pressure, the overall size increases. On the other hand, in the hydraulic motor mode, if the inlet pressure exceeds the outlet pressure and the moment when the transport hole joins the outlet hole coincides with the positive rising front of the pressure wave, the value of the shift angle increases, The value of the reference angle approaches the separation angle of this transport hole from the outlet hole. However, if the instant coincides with the negative falling front of the pressure wave, the value of the shift angle decreases and the reference angle approaches the angle at which this hole meets the outlet hole. The shift angle can be adjusted, for example, by changing the opening / closing moment of the control valve 18. As the magnitude of the outlet pressure wave increases, the range of shift angle changes also increases.

If the leaks are the same for all transport holes, the shift angle is selected equally for all holes. However, if different transport holes have different leak rates, selection of different values for the shift angles of the different transport holes can compensate for the leak range. The overall magnitude of the change in capacity of the transport hole (curve 16a in FIG. 8) is selected according to the average rate of leakage (curve 16c). For equal shift angles, the compensatory comparison flow is φ = φ _ref = φ _merg. -Φ _shift equalizes the transport hole pressure, but at the moment of merging at the exit hole, the difference in leakage widens the transport hole pressure (curves 17b, 18b), leaving different signal waves. In order to compensate for different leak rates, the shift angles for the different transport holes are selected differently. In the pump mode for transport holes (curves 18c, 18d) where the rate of leakage exceeds the average level in all transport holes (curve 16c), the shift angle φ _shift 2 exceeds the average shift angle φ _shift 0. For holes (curves 17c, 17d) with a leak rate that is less than or equal to the average level of all the transport holes, the shift angle φ _shift 1 is less than or equal to the average shift angle φ _shift 0, and the leak range is compensated. For holes where the rate of leakage exceeds the average rate (curve 18c), the shift angle φ _shift 2 is larger, and at the reference angle, φ _ref 2 = φ _merge. 2-φ _shift 2 and the pressure Pi (φ _ref 2) becomes equal to or lower than the reference pressure P _ref (P _out 0). Therefore, the compensatory comparative flow moves from the first hole 16 of the hydraulic cylinder 15 to this transfer hole, reducing the mass of the working fluid in the hole 16 and reducing the mass and pressure of the working fluid in the transfer hole (curve 18c). Increase and compensate for the loss of working fluid caused by the high leakage rate from it. For holes where the leak rate is below average (curve 17c), a smaller shift angle φ _shift 1 is selected, so that at the reference angle, φ _ref 1 = φ _merg. −φ _shift 1, and the pressure Pi (φ _ref 1) becomes higher than the reference pressure P _ref (P _out 0). Therefore, the compensatory comparative flow moves from the transport hole to the hole 16 and decreases the mass and pressure of the working fluid in the transport hole and increases the mass of the working fluid in the first hole 16 of the hydraulic cylinder 15 at a low leakage rate. This compensates for the loss of working fluid taken at a high leakage rate and then by a compensatory comparative flow to the transport holes. In the hydraulic motor mode, the opposite dependence of the shift angle on the leakage rate is applied. The leak rate can be detected, for example, by measuring the pressure in the transport hole. In the preferred embodiment, for each conveying hole, the wave of the outlet pressure is detected at the moment when it merges with the outlet hole, and the reference angle of this conveying hole is selected according to the magnitude and phase of the wave as described above. I will provide a.

The present invention relates to a method for adjusting the overall angle. The present invention adjusts the angle range in which the conveying hole is separated from the inlet hole and the outlet hole, and the change in the capacity of the conveying hole changes its pressure, φ _total = φ _merg. The -.phi _detach, also provides a method of adjusting the variation range of the pressure of the transport pores. The overall magnitude of the change in the capacity of the transport hole A _total in this adjustment method is selected according to the maximum difference and the maximum movement between the inlet pressure and the outlet pressure. The corresponding changes in the capacity of the transport hole and the pressure of its working fluid are shown in FIG. 9 (curves 19a, 19b). With the maximum pressure drop dP and movement, the overall angle φ _total is also maximum. As dP or movement changes, the overall angle φ _total also changes, that is, as dP or movement decreases, φ _total decreases, and as these characteristics increase, the overall angle increases.

There are two variations for adjusting the overall angle φ _total .

In the first modification, φ _merg. Is changed by connecting the transport hole to the outlet hole in advance at the moment when the pressure of the transport hole becomes equal to the outlet pressure. As a previous result, further changes in the pressure of the working fluid in the transport hole stop (curves 20b, 21b in FIG. 9). Connecting the transport hole to the outlet hole in advance can be performed by moving a blade separating the transport hole from the outlet hole or by connecting the transport hole to the outlet hole via a normally closed bypass duct. It is. In the latter case, starting from the moment of the open bypass duct, a part of the fluid is moved from the conveying hole to the outlet hole via the bypass duct (curves 20c, d, 21c, d in FIG. 9) (hydraulic For motors, from the exit hole to the transport hole). The bypass duct is opened using, for example, a pressure sensor and an electric control valve. The preferred embodiment of the present invention uses a bypass duct back pressure valve that is opened when the pressure differential signal between the ends of the bypass duct changes.

In the second embodiment, the overall magnitude Atotal is selected (corresponding to the maximum value of the curves 22a and 22b in FIG. 10), that is, the maximum value of dP and the maximum value of movement of the device. As the movement changes, _φdetach changes due to delayed separation from the inlet hole of the transport hole. The change in _φdetach can be performed as follows. The transport holes transported from the inlet holes to the outlet holes remain connected to the inlet holes within the selected angular movement (curves 23b-d, 24b-d). Said delay can be realized by changing the movement characteristics of the vanes leading to delayed separation by this vane to the inlet hole of the conveying hole or by connecting the conveying hole to the inlet hole via an openable bypass duct. is there. In the latter case, up to the moment when the bypass duct is closed, a part of the fluid passes through the bypass duct (curves 23c, d and 24c, d in FIG. 10) from the outlet hole to the inlet hole (in the hydraulic motor, the inlet hole). Move from hole to transport hole). The bypass duct is opened using, for example, a pressure sensor and an electric control valve. The preferred embodiment of the present invention adjusts _{φdetach according} to the magnitude and phase of the pressure wave in the outlet hole. In the pump mode, if the outlet pressure exceeds the inlet pressure, this is achieved as follows. If the moment when the conveying hole merges with the outlet hole coincides with the positive rising front of the pressure wave (curve 8 in FIG. 2), φ _detect increases, ie, the delay increases, but the moment negative when matching the falling front (curve 5, 7) of, phi _detach decreases. In the hydraulic motor mode, when the outlet pressure is below the inlet pressure, if it coincides with the positive rising front of the pressure wave (curve 8 in FIG. 2), _φdeatch will be negative at the negative falling front at the moment. Increase and decrease at the positive rise front.

  In both embodiments, the resistance of the bypass duct is selected such that the fluid flow along the bypass duct, which is important from the point of view of the invention, does not cause a pressure drop between the ends of the bypass duct. The

  In order to make the pressure of the working fluid in the rear transport hole equal to the inlet pressure at the moment when the rear transport hole joins the inlet pressure, the current rear transport hole is within the range of the rotation angle of the rotor separated from the outlet hole and the inlet hole. There is a similar solution for coordination. When the overall size Atotal is constant, the range of the rotor rotation angle for each method transport hole is increased by increasing the difference between the outlet pressure and the inlet pressure and decreased by decreasing the difference. If the overall size Atotal is increased when the movement is increased, the maximum value of the range of the rotor rotation angle corresponds to the maximum movement, and the range of the rotor rotation angle is decreased when the movement is increased. Is done.

Sinusoid's Law of Change in Capacity of Transport Hole In the preferred embodiment of the present invention, it is shown that the capacity of the transport hole is changed by the angular movement of the transport hole according to the law of sinusoid. The angular movement of each i transport hole means an angle φ _i measured in the direction of rotation of the rotor from that position of the rotor, which transport hole is equidistant from the inlet and outlet holes. The sinusoidal law or sine function here is the angular movement of the transport hole Ai (φ _i ), which supplies an absolute value a ₁ that exceeds the absolute value of all other expansion coefficients a _k and b _k with an extension of the Fourier series. Is understood as such a dependency of the variable part of the capacity.

本発明の実施の形態の１つは、これにより制限される円の中心を通る直線の一部分の長さと搬送孔の容量を変える第１の円の半径よりかなり小さい値分移動シフトされた中心を有するより大きな直径の別の同一平面上の円とのシヌソイドの角度の依存関係を使用している。

One embodiment of the present invention has a center shifted and shifted by a value much smaller than the radius of the first circle that changes the length of the portion of the straight line passing through the center of the circle and the capacity of the transport hole limited thereby. Using the sinusoidal angle dependency with another larger coplanar circle of greater diameter.

  The use of a cylindrical surface of the housing having an axis that is parallel and shifted with respect to the rotor's axis of rotation for sinusoidal change in the capacity of the transfer hole is similar to adjusting the movement of a radial piston or radial sliding vane pump. By changing the shift of the shaft, it is allowed to change the range of change in the capacity of the transport hole. The present invention uses the shifted cylindrical surface of the housing as the surface of the guide cam of the movable wall drive mechanism of the forced chamber.

  Another embodiment uses a sinusoidal angle dependency of the length of the line segment limited to a cylindrical surface by a plane perpendicular to the axis of the cylinder and a plane inclined at a small angle towards the surface. Yes.

  The use of a housing surface that is inclined at a small non-zero angle with respect to a plane perpendicular to the rotor's axis of rotation due to the sinusoidal change in the capacity of the transfer hole results in an inclination angle similar to the adjustment of axial piston pump movement. By changing, it is allowed to change the range of change of the capacity of the transport hole. The present invention uses the surface of the inclined surface of the housing as the guide cam surface of the movable chamber drive mechanism of the forced chamber.

  The preferred embodiment of the present invention (FIG. 4) uses a support portion of a rotor 13 that rotates with the actuating portion of the rotor 2 and is attached with the possibility of tilting to it. In the plane passing through the outlet hole 7, the mutual inclination of the rotor support part 13 and the axis of rotation of the actuating part 2 provides a periodic change in the capacity of the forced chamber 10 according to the sinusoidal law.

  The sinusoidal law of change in the capacity of the variable capacity transport hole is that the second kinematics of the transport of the rotor sliding blade device by periodically changing the overall capacity of the hole connected to the outlet hole and the inlet hole. Inhomogeneity occurs (FIG. 4). The non-uniformity of the transport has sharp and sharp changes in the transport at the two types of exit holes (curve 25 in FIG. 11). The first type << a >> jump occurs at the exit hole at the moment when the transport hole joins the exit hole. The second type << b >> jump occurs at the exit hole at the moment the rear transport hole separates from the exit hole. If the separation from the outlet hole of the rear conveying hole occurs at the same time as the conveying hole joining the outlet hole, the second type of conveying jump occurs simultaneously with the first type of jump, resulting in the overall size of the conveying. Increases (curve 26 in FIG. 12). In a pump, the jump increases transport. In the interval << c >> between sudden increases in transport, the transport gradually decreases.

FIG. 12 shows an example of the second kinematic non-uniformity of the transport of a rotor sliding blade pump with 13 blades, with a pumping pressure of 40 MPa and 0.001 MPa ⁻¹ characteristic of hydraulic oil. Corresponding to the compression rate of the working fluid, the capacity of the conveying hole is 7 cm ³ at the inclination angle of the support portion of the rotor, and the total capacity of the outlet hole, the rotor hole connected thereto and the labyrinth of the housing is 32 cm. Equal to ³ . With zero change in the mass of the working fluid in the transfer hole, the second kinematic non-uniformity is about 2% of the pump transfer when the first and second types of transfer jumps occur simultaneously. have. If the first and second types of transport jumps do not occur simultaneously, the second kinematic non-uniformity is reduced (curve 25 in FIG. 11). A second type of jump occurs in the middle of the first type of jump. The second kinematic non-uniformity of the jump will be about 1%.

If the capacity of the duct to jump is close to zero, i.e., the addition of inlet capacity of zero, for example, if the diaphragm is arranged immediately adjacent to the outlet of the pump, the total outlet capacity of the 32cm ^3, both in the case of The kinematic non-uniformity is correspondingly converted to a pressure fluctuation of 1% (curve 27) or 0.2% (curve 28) of the pumping pressure (FIG. 13). Under the same conditions, the initial pressure wave caused by decompression exceeds 11% (curve 29). Therefore, the sinusoidal change in the capacity of the pressure conveying hole that supplies the pressure equalizing the conveying part to the outlet hole due to the complete disappearance of the power loss due to the merging and decompression of them reduces the pressure wave by 10 to 50 times, Improve the uniformity of flow generation.

As the capacity of the pumping duct increases, the pressure wave caused by the kinematic inhomogeneity of the transport decreases (FIG. 14). Even with a relatively small capacity of the pumping duct equal to 320 cm ³ , the pressure waves range from 1% (curve 27 in FIG. 13) to 0.2% (curve 30 in FIG. 14) and 0.2% (curve 28 in FIG. 13). To 0.05% (curve 31 in FIG. 14) to produce a uniform working fluid flow. A further increase in the capacity of the pumping duct improves the flow uniformity and reduces the pressure waves generated by the second non-uniformity of the transfer to a negligible value.

Compensatory flow In order to improve the uniformity of the generated flow of working fluid with a small capacity of the pumping duct, the present invention provides at least a working fluid between one of the transport holes and the outlet hole via the compensatory duct. By generating one compensatory flow, the second non-uniformity of transport described above is compensated.

  In order to compensate for the above-mentioned transport jump of the first type, the present invention merges the current transport hole 9 with the outlet hole 7 after the separation of the next transport hole from at least one inlet hole 6, A first compensatory flow of working fluid is created between the conveying hole and the outlet hole following the current hole via the first compensatory duct 19 at the moment of confluence with the outlet hole of the conveying hole (FIG. 15).

  Compensation of the flow due to simultaneous merging with the outlet hole of the conveying hole, for example, using a slip valve selection device or a solenoid valve, the rotor of the rotor corresponding to the moment of merging with the outlet hole of the other conveying hole. This is realized by connecting a compensatory duct to the transport hole at a fixed angle of rotation φcompens.

  FIG. 16 shows the compensation in the angular motion of the transport holes in the absence of compensatory flow (curves 32a-32d) and in the case of compensatory flow between the exit holes and the closest transport holes (curves 33a-33d). Flow ratio DRi (φ) (FIG. 16a), change in mass of transport hole DMi (φ) (FIG. 16b), capacity Vi (φ) of transport hole (FIG. 16c), and pressure Pi (φ) of the transport portion FIG. 16d shows the dependency relationship.

  In this case, the pressure difference between the ends of the compensatory duct gradually changes at the same time as the first type of jump from the variable capacity hole of the outlet hole to the outlet hole, and through the compensatory duct. Cause a corresponding jump in the proportion of compensatory flow of working fluid from the outlet hole (curve 33a).

  The hydraulic resistance of the compensatory duct is selected such that the compensatory flow rate jump from the outlet hole and the jump of the first type of transport are equal and compensate for each other. The second kinematic non-uniformity value of the transfer is proportional to the rotational speed of the rotor. Thus, increasing the rotational speed of the rotor increases the hydraulic resistance of the compensatory duct and vice versa. If the overall magnitude of the change in capacity of the transfer hole is changed due to the change in movement of the rotor sliding blade device, the increase in movement will increase the hydraulic resistance of the compensatory duct and vice versa. . When the maximum range of the angle at which the transport hole is separated from the outlet hole and the outlet hole is changed due to the change of the difference between the outlet pressure and the inlet pressure dP, the increase in dP increases the hydraulic resistance of the compensatory duct. And vice versa.

  Similarly, it is possible to compensate for jumps in the second type of transport. For this purpose, at the moment when the current rear conveying hole separates from the outlet hole, a second compensation for working fluid is provided between one of the subsequent conveying holes and the outlet hole via a second compensatory duct. Flow will occur.

The creation of a compensatory flow between the outlet hole and the transport hole changes the mass of the working fluid in the transport hole, rapidly increasing the pressure difference between the ends of the compensatory duct (curve 33d), and Increase the rate of general flow (curve 33a). The increase in the fluid mass of the transfer hole compared to the first change (movement from curve 32b to curve 33b in FIG. 16) to achieve the same Pout (curve 32d with no compensatory flow and compensation) (See curve 33d with a general flow) This leads to the need to increase A'total compared to the first Atotal (movement from curve 32c in FIG. 16 to curve 33c). Compensatory flow rate drop characteristics (curve 33a shows the rate of flow to the transport holes, curve 34 in FIG. 17 is the fluid rate from the exit holes, they are equal in value and the trajectory is opposite. .) And the second non-uniformity reduction characteristic of the transport between the jumps (curve 35 in FIG. 17) determines the level of remaining kinematic non-uniformity of the transport. In the example of the pump described above that is configured so that the first and second types of transport jumps occur simultaneously, the rotational speed of the rotor of 3000 rpm and the hydrodynamics of the compensatory duct of 0.5 MPasec / cm ^3. With the mechanical resistance, the generation of compensatory flow between the outlet hole and the nearest conveying hole reduces the level of conveying kinematic non-uniformity from 2% (curve 35) to 0.3% (curve 36). Decrease. Even for the zero capacity example of the outlet duct described above, the pressure oscillation level is 0.1% (curve 37 in FIG. 18), where the working fluid flow generated from 1% (curve 27) is considered almost completely uniform. Reduced to

  In order to further reduce the remaining kinematic non-uniformity of the transfer, the present invention allows the current transfer hole to merge with the exit hole after separation from the inlet hole of at least two subsequent transfer holes (FIG. 19). A compensatory flow of working fluid occurs between the second or subsequent of the next transport hole and the exit hole via the compensatory duct 19 and has a selected hydraulic resistance. A compensatory hole 20 of a selected volume separated from the outlet hole 7 by a path is provided. FIG. 20 shows a compensatory flow from the compensatory hole to the transport hole in the angular motion of the transport hole in the absence of compensatory flow (curves 39a-39e) and in the case of compensatory flow (curves 40a-40e). Dependency of the flow rate ratio DRi (φ) (FIG. 20a), dependency of the compensatory flow rate DRac (φ) from the outlet hole 7 to the compensatory hole 20 (FIG. 20b), change in mass of the transport hole DMi (Φ) (FIG. 20c), the transfer hole capacity Vi (φ) (FIG. 20d) and the transfer hole pressure Pi (φ) (FIG. 20e) are shown. When the more linear characteristic of the compensatory flow drop (curve 40b) reproduces more of the second non-uniform transport drop characteristic (curve 35 of FIG. 17), the second kinematic non-uniform It can be seen that better complete compensation of transport is possible in this case.

  As the compensatory hole volume increases, the level of remaining non-compensatory non-uniformity decreases, but the overall size Atotal decreases and the working fluid merges with the current transfer hole of the compensatory hole. The level of dissipative power loss caused by the effects of depressurization (see compensatory flow jump in curve 40a and pressure jump in curve 40e) and the loss of hydraulic resistance in the compensatory duct is high. Compensation duct capacity, including compensatory hole Vac capacity, is optimal between the level of dissipative power loss and the level of remaining non-compensatory kinematic heterogeneity in the transport for a particular application. Is selected based on the percentage. Compensatory duct resistance at a set capacity is selected as described above.

In the example of the pump described above, application of such a method with a hydraulic resistance of 0.05755 MPa · sec / cm ³ at a capacity of 297 cm ³ reduces the oscillation of the outlet pressure to a value of around 0.001%, ie Even with the above-mentioned condition of zero capacity of the outlet duct, the flow is completely uniform.

Apparatus An apparatus provided for carrying out the above method for generating an undulating flow of working fluid comprises a housing 1 having an inlet 24 and an outlet 25 (FIGS. 21-23, 29-34), the housing Comprises an actuating cover plate 21 having a front transport limiter 5 and a rear transport limiter 22 thereon. The device also comprises a rotor having a vane chamber 3 formed in the working part 2 of the rotor and a vane 4 formed in the working surface of the rotor and kinematically connected to a blade drive mechanism attached to the housing. And an annular groove 23 connected to the blade chamber 3. The rotor also includes a variable volume forced chamber 10. The operating cover plate 21 of the housing is in sliding insulating contact with the operating surface of the operating part of the rotor 2 and forms an operating chamber in the annular groove 23. The rear conveying insulating rotor means slidingly contacting the rear conveying limiter 22 and the front conveying insulating rotor means including the front conveying limiter 5 and the blade conveying sliding insulating contact are separated from each other and hydraulically connected to the inlet 24. It becomes an inlet hole 6 and an outlet hole 7 that is hydraulically connected to the outlet 25 and at least one transport hole 9. Each transport hole 9 is formed by an inner blade hole 8 and is coupled to the annular groove 23, the front transport limiter 5 and two adjacent blades 4, and the surface of at least one forcing chamber 10 connected to this inner blade hole 8. The Each of the transport holes 9 corresponds to an individual range of the rotation angle of the rotor, and the transport holes 9 are separated from the inlet hole 6 and the outlet hole 78. The working fluid confined in the conveying hole forms a conveying portion of the working fluid. In order to implement the above method of generating an undulating flow of working fluid, the apparatus has a capacity of the forced chamber 10 at the rotational angle of the rotor to which it is connected to the inlet hole and the rotation to which it is connected to the outlet hole. It is provided with a capacity changing means formed with the possibility of changing the ratio between the same forced chamber volume at different rotation angles of the child.

  The present invention is an embodiment of an apparatus suitable for use as a pump or hydraulic motor and a hydrodynamic transmission pumping motor unit. In some embodiments, the housing is fixed to the collective rack and the rotor rotates relative to the housing and the collective rack. In other embodiments, the rotor can be secured to a collective rack having a housing that rotates relative thereto. For example, if the device is a hydrodynamic transmission unit, there is another possible embodiment with a housing that rotates relative to the rotor and the collecting rack. In any case, the rotor or rotor unit has an annular groove in the surface element and includes vanes that circulate with the rotor each time the rotor rotates and change their extent of projection into the annular groove. It means a unit that is out. By housing or stator unit is meant a unit for which the inlet and outlet positions do not change with the mutual rotation of the rotor and housing.

  The capacity variable means that may change the capacity of the forced chamber within the above range of the angular movement of the transport hole is, for example (FIG. 3), attached to the housing 1 in a movable wall of the variable capacity forced chamber 10. It is possible to form a cam mechanism 12 that is in sliding contact with 11.

An apparatus having a support part of a rotor In order to carry out the method of changing the sinusoid of the capacity of a transport hole, a preferred embodiment of the present invention (FIG. 4) is based on the kinematics of the working part of the rotor 2 by assembling the rotor element. Providing a support part for the rotor 13 to be connected in a fixed manner, with a variable capacity actuating part that rotates in the axial direction and rotates simultaneously with the actuating part of the rotor. Yes. The volume of the forced chamber 10 is changed by the above-described operation of the support portion of the rotor 13 with respect to the operation portion of the rotor 2. The capacity changing means of this embodiment includes means for tilting the rotation shaft of the support portion of the rotor with respect to the rotation shaft of the operating portion of the rotor 2. The rotation axis of the rotor support portion relative to the rotor operation portion at an angle γ (FIG. 4) located in the plane passing through the rotation axis and the inlet and outlet holes of the rotor operation portion is the rotation of the rotor. A sinusoidal change in the volume of the forced chamber 10 is generated. The magnitude of the change in capacitance is proportional to the tangent of the mutual inclination angle of the rotating shafts.

  In order to adjust the change of the capacity of the forced chamber, the tilting means comprises a tilt angle changer comprising a moving element kinematically connected to the support part of the rotor, and the movement of the rotor by the movement of the element The inclination angle of the rotating shaft of the support portion of the rotor with respect to the rotating shaft of the portion is changed.

  The preferred embodiment of the present invention from the viewpoint of volumetric efficiency at a low rotational speed of the rotor is a rotary thrust bearing having an operating portion of the rotor 13 to which a tilting means of a rotating shaft of a support portion of the rotor 13 is attached. 26 is provided (FIG. 21). The rotary thrust bearing is formed, for example, in the form of a rolling bearing.

  In order to adjust the overall magnitude of the change in the capacity of the transport hole, the invention in this case has the possibility of tilting, i.e. a straight line passing through the rotating shaft of the working part of the rotor and the front and rear transport limiters The housing carrier 27 of the rotary thrust bearing 26 is mounted with the possibility of rotation relative to the working cover plate 21 of the housing around an axis parallel to the axis. The tilt angle changer comprises a moving element in the form of a piston 14 of a working hydraulic cylinder 15 which is kinematically connected to a housing carrier 27 of a rotary thrust bearing 26, the movement of the piston 14 with respect to the hydraulic cylinder 15 being the axis of said shaft. The carrier 27 is rotated around, and the inclination angle of the rotation shaft of the support portion of the rotor 13 with respect to the rotation shaft of the operation portion of the rotor 2 is changed.

  In order to reduce wear of the support part of the rotor due to the inclination of the rotation axis with respect to the rotation axis of the working part of the rotor, the forcing chamber has a flat surface in sliding contact with the flat surface of the right part of the support part of the rotor 13 , Kinematically connected to the support part of the rotor via a load bearing joint element formed as a sliding element 29 having a convex spherical surface of the movable wall of the forced chamber 10 and a concave spherical surface in sliding contact.

  A preferred embodiment of the present invention from the viewpoint of reducing friction loss and overcoming cavitation tendency at high rotational speed of the rotor (FIG. 22) is a support cover plate of the housing that is in sliding insulation contact with the support portion of the rotor 13. 30 is provided with a tilting means for the rotating shaft of the support portion of the rotor. The support cover plate 30 is formed with an insulating barrier 59 (FIG. 32) opposite to the front transfer limiter 22 and the rear transfer limiter 22 of the operation cover plate 21. In order to reduce friction loss, a support hole 32 is formed between the support cover plate 30 of the housing and the support portion of the rotor 13 so that an insulating means is provided. In this case, each transport hole 9 is connected to at least one support hole 32. The support holes 32 improve the hydraulic balance of the support portion of the rotor 13 and reduce friction loss.

  The present invention provides two types of structures for the apparatus for generating an undulating flow of working fluid comprising a support cover plate of the housing.

  The structure of the first type of device is in the traditional configuration of a rotor hydrodynamic device having a rotor arranged between the housing operating cover plate 21 and the support cover plate 30 connected by a connecting element of the housing. It corresponds. The connecting element can traditionally be formed as a hollow body with a rotor arranged therein. There is an embodiment with a through-opening in the rotor having a connecting element of the housing passing therethrough.

  In the device corresponding to the second type of construction (FIGS. 23a, b, c), the housing support cover plate 30 and the housing actuating cover plate 21 are arranged between the actuating part 2 and the supporting part 13 of the rotor. A housing operating unit 33 is formed and coupled. The operating unit of the housing can be formed as an integral part. In such an embodiment, the role of the actuating cover plate is performed by the surface of the operating unit in sliding insulating contact with the actuating surface of the actuating part of the rotor, and the function of the support cover plate is with the supporting surface of the supporting part of the rotor. Performed by the opposite surface of the operating unit in sliding insulation contact. In a second type of construction, the present invention comprises a rotor coupling element 34 in which the assembly of rotor elements used to connect the working part 2 and the support part 13 of the rotor. In the first embodiment, the housing operating unit 33 has a through opening through which the rotor coupling element 34 passes. In the second embodiment, the rotor coupling element is formed outside the operating unit of the housing attached to a bearing element such as a shaft, and passes through the through-opening of the working part or support part of the rotor. The compulsory chamber 10 can be arranged on both sides of the operating part side of the rotor and the support part side of the rotor. The device has a groove that is shaped for connection of the support hole 32 to the inner vane hole 8. These grooves can be formed in the connecting element 34. A preferred embodiment is provided for forming a groove 89 in the operating unit 33 of the housing and includes a groove in the forward transport limiter 5. In order to prevent decompression loss of the fluid when the groove 89 joins the transport hole 9, the groove 89 is formed so that the capacity of the groove 89 forms a portion where the capacity of the transport hole 9 can be ignored.

  22 and 23, the support hole is formed in the support portion of the rotor 13 and is separated by an insulating barrier 31. In a particular embodiment, the support part of the rotor is formed in the same way as the working part of the rotor, i.e. it is arranged in the annular groove and the blade chamber, closing the annular groove and dividing it into individual internal blade holes. And from the standpoint of hydraulically balanced, it is also equipped with blades equivalent to the support holes. In this case, the insulating barrier of the support cover plate opposite to the front and rear transport limiters of the working cover plate is formed as a front and rear transport limiter, and the annular groove is provided between the support portion of the rotor and the support cover plate of the housing. A second working chamber is formed. In such an embodiment, the provided invention considers one of the two said parts of the rotor as an actuating part and correspondingly the other is considered a support part.

  The present invention also provides an embodiment (FIG. 25) in which the support holes 32 are formed in the support cover plate 30.

  Both the structure with the support part of the rotor sliding along the support cover plate of the housing and the above-mentioned type of modification of the embodiment of the support hole are described in the "Rotation" of Russian application 200511013098 of 26 April 2005. This is described in detail in “Sliding Device”.

  Even if either of the two types of structures described above is implemented in an apparatus that includes a support cover plate for the housing, the present invention adjusts the overall magnitude of the change in the capacity of the transport holes. For this purpose, the housing support cover plate 30 (FIG. 24) is mounted with the possibility of rotation relative to the housing cover plate 21 about the axis 36, parallel to a straight line passing through the front and rear transport limiters. It has been. The tilt changer includes a moving element 28 kinematically connected to the support cover plate 30, and the support cover plate 30 is rotated around the axis by the movement of the element 28, so that the rotation axis of the working part of the rotor is rotated. On the other hand, the inclination angle of the rotating shaft of the support portion of the rotor is changed.

Embodiments of an apparatus for carrying out the overall size adjustment method In order to carry out the overall size adjustment method, the tilt angle changer changes the flow parameter of the working fluid into the movement of the moving element. Includes converting.

  In order to carry out the above-described method for adjusting the overall magnitude of the change in the capacity due to the difference between the outlet pressure and the inlet pressure, the changer of the tilt angle of the rotation shaft of the support portion of the rotor is caused by the movement of the element. The pressure difference between the inlet hole and the outlet hole to the movement of the moving element kinematically connected to the support part of the rotor with the possibility of changing the tilt angle of the axis of rotation of the support part of the rotor It has a converter. The transducer can be filled with hydraulic fluid, for example, using a pressure sensor and an electric drive source or under a calibrated spring and pump outlet pressure (under inlet pressure, for hydraulic motors). Formed using a cylinder piston.

  In order to carry out the adjustment method of the overall magnitude of the change in the capacity of the transport hole due to the difference between the reference pressure and the pressure of the transport hole at the reference angle, the present invention provides the support portion of the rotor by moving the element. The difference between the reference pressure for the movement of the moving element kinematically connected to the support part of the rotor with the possibility of changing the tilt angle of the rotary shaft and the pressure of the current conveying hole at the reference angle The tilt angle changer including the converter is provided. The reference pressure is equal to a selected value between the inlet pressure and the outlet pressure, and the reference angle is in the range from the inlet hole separation angle of the current transfer hole to the merging angle of the current transfer hole with the outlet hole. Selected.

  The transducer is formed using a pressure sensor and an electrical drive source. In a preferred embodiment, the transducer is made with the possibility of a hydraulic connection to the transfer hole via a hydraulic actuator, for example a control valve, and an outlet (for a hydraulic motor to the inlet hole). Formed as a double-acting hydraulic cylinder that is hydraulically connected to the bore. In one embodiment of the present invention (FIG. 6), the hydraulic actuator has a differential double-acting hydraulic power having a first hole 16 connected to the control valve 18 and a second hole connected to the outlet hole 7. Formed as a cylinder 15. The control valve 18 includes an electric drive source, for example, a solenoid, and an electric control system that provides an opening of the control valve 18 at the moment coincident with the rotor rotation angle equal to the reference angle. The use of a solenoid valve with electrical control as a control valve that can be opened and closed at the moment specified for each transport hole provides maximum flexibility in shift angle depending on the rate of leakage. However, such a valve will open and close many times during one revolution of the rotor, and the operating speed of such a valve will limit the possibility of adjusting the shift angle with the high speed rotation of the rotor.

In another embodiment of the present invention (FIG. 25), the control valve is the first of the rotor unit of the device that is hydraulically connected to the first hole 16 of the differential double-acting hydraulic cylinder 15. The control valve is formed as a control slide valve selector having a stator window of the first surface slide valve 38 and a rotor window of the second valve slide valve 39 of the rotor unit of the apparatus, each conveying hole being one of the slip valves. It is connected hydraulically to the two rotor windows. The first and second surfaces are in sliding insulating contact with each other with the possibility of a hydraulic connection of each rotor window of the slide valve to the stator window of the slide valve. The connection of the conveying hole to the first hole of the differential double-acting hydraulic cylinder in this case occurs when the corresponding rotor window coincides with the stator window of the slip valve selector. The shift angle in this case is set by the mutual position of the sliding valve windows of the rotor unit and the stator unit. In order to adjust the shift angle with the high speed rotation of the rotor, the present invention relates to an apparatus formed with the possibility of hydraulic connection of each rotor sliding valve window 39 to the stator window of the sliding valve 38. The use of a control slip valve selector in assembling the stator slip valve window 38 on the first surface of the stator unit is provided. Each stator window of the slide valve 38 is hydraulically connected to a selector switch 40 of the stator window that is hydraulically connected to the first hole 16 of the differential double-acting hydraulic cylinder 15. One of the stator sliding valve windows is selected by the rotor rotation speed, the viscosity of the working fluid, and other characteristics that affect the leakage rate from the transfer hole, and the first of the hydraulic cylinders 15 via the selector switch 40 is selected. The holes 16 are connected hydraulically. Thereby, one shift angle is selected from one set of shift angles. The selector can be formed, for example, as a solenoid distribution valve. In the device shown in FIG. 25, the rotor slip valve window 39 is connected to both the stator slip valve window 38 and the support holes 32 formed in this case in the support cover plate 30 of the housing.

  In order to carry out the adjustment method of the overall size of the transfer hole capacity conversion according to the magnitude and phase of the vibration of the outlet pressure, the present invention provides an inclination angle of the rotation shaft of the support portion of the rotor by the movement of the element. Implementation with a tilt angle changer with a magnitude and phase converter of the oscillation of the outlet pressure to the movement of the moving element kinematically connected to the support part of the rotor with the possibility of changing Provide the form. The transducer is formed using, for example, a pressure vibration sensor, a phase detector and an electric drive source. "Detailed description of the apparatus and operation of an embodiment of the proposed invention" part has the converter formed in two stages, implementation with two converters electrically connected to each other This form will be further described. The first is a magnitude and phase converter for the oscillation of the outlet pressure to a shift angle that determines the reference angle for each transport hole, and the second is between the reference pressure and the pressure of the transport hole at the reference angle. It is a transducer that moves to the above-mentioned moving element of the difference.

  In order to adjust the volume of the working fluid moved by the movement, i.e. the device from inlet to outlet per revolution of the rotor, and to change the overall size by changing the movement, the present invention Providing a forward transport limiter that is made movably to the annular groove and has a mechanism for changing the forward transport limiter into the annular groove, the tilting means of the rotating shaft of the support portion of the rotor is in the axial direction of the forward transport limiter Is formed with the possibility of changing the tilt angle of the rotation axis of the support portion of the rotor when the position of the rotor is changed.

Apparatus with a compensation duct In order to carry out the method of compensating for the second kinematic non-uniformity of the transfer by means of creating a compensatory flow of working fluid between the transfer hole and the outlet hole, the present invention comprises: The blades are made in sliding insulating contact with the forward transport limiter so that at least two transport holes can be separated from the inlet and outlet holes at the same time, and the outlet holes are hydraulically connected to the transport holes via a compensation duct with a compensating throttle. Hydraulically connected to a compensating valve that is formed with the possibility of mechanical connection.

  The compensation valve is formed, for example, as a solenoid valve that is electrically connected to a sensor for the rotation angle of the rotor. A preferred embodiment of the present invention (FIG. 15) provides the compensation valve formed as a slip valve selector formed by the distribution path 41 and the vanes 4 of the forward transport limiter 5. In the rotation of the rotor, the vanes block the distribution path 41 connected to the current transport hole and connect it to the next transport hole which creates a compensatory flow between this next transport hole and the outlet hole. . In the described embodiment with the housing support cover plate, the distribution path formed in the housing support cover plate with the possibility that the slip valve selector is connected to the support hole at the support portion of the rotor, and the rotation It is formed in the support portion of the child, and can be formed by the insulating means of the support hole in sliding contact with the support cover plate of the housing with the possibility of blocking the distribution path by the rotation of the rotor.

  In order to adjust the hydraulic resistance of the compensation duct, the throttle 42 is provided with means for changing its hydraulic resistance X. In order to carry out the method of improving the accuracy of the compensation of the second kinematic non-uniformity of the conveyance, the present invention comprises at least one separated from the outlet hole 7 by at least one of the compensation throttles 42 The compensation duct having the compensation hole 20 is provided (FIG. 19). The compensation hole 20 can have means for changing its capacity.

Embodiment of the device for the implementation of the overall angle adjustment method In order to carry out the overall angle adjustment φ _total method described above, the device of the present invention has the possibility of a hydraulic connection to the transport hole And a global angle adjustment means comprising either at least one bypass path with an overall angle adjustment valve or a vane attached to the rotor with the possibility of changing the overall angle . In the following, an embodiment of an overall angle adjusting means for executing both modifications of the above-described overall angle adjusting method will be described.

_Delivery hole outlet hole φ _merg. In order to execute the above-described overall angle adjusting method by changing the merging angle with the valve, the overall angle adjusting valve is formed with a possibility of being hydraulically connected to the outlet hole. φ _merg. In order to regulate, the present invention provides two embodiments of the valve. In the first embodiment (FIG. 26), the overall angle adjusting valve 43 is formed in the front limit bypass path 44 of the stator unit, one end of the path 44 communicates with the outlet hole 7, and the other end of the path 44. Enters the forward conveying area with the possibility of being connected to the conveying hole 9. The valve 43 is formed with the possibility of opening the path 44 when the pressure drop sign between the ends of the path 44 is changed. φ _merg. In the second modification of the adjustment, an overall angle adjustment valve is formed on the rotor. The preferred embodiment of the present invention uses vanes as movable elements of the overall angle adjustment valve. In this case, each of these blades is moved by opening the transfer hole when the pressure drop sign between the two transfer holes separated by this blade is changed, and the pressure is changed to the pressure in the outlet hole. It is formed to exceed. FIG. 4 shows a cross section of a rotor with axially movable vanes attached to the vane chamber 3, which is connected to the vane drive mechanism with the possibility of axial backlash. In order to self-seal the blade sealing material 45 that slides along the front transport limiter 5, the holes arranged in the blade chamber 3 from the side of the blade opposite to the sealing material 45 are transported through the path 46 in front of the blade. Connected to hole 9, which replaces the flow from it with a pumping hole (in hydraulic motors said hole is connected to the conveying hole after the vane). The pressure of the conveying hole 9 after the blade 4 separated by the blade from the outlet hole 7 is equal to or lower than the pressure of the outlet hole, the force acting on the opposite surface of the blade 4 exceeds the force acting on the sealing surface 45, and the blade 4 Is pressurized to the forward conveyance limiter 5. As soon as the pressure in the transport hole 9 after the blade exceeds the pressure in the outlet hole 7, the blade 4 is pushed in from the front transport limiter 5 to open the transport hole. FIGS. 23a, b, c are rotors with axially rotating blades attached to the blade chamber and formed with the possibility of bending the elastic element 47 of the blade 4 when the pressure drop sign is changed. The cross section of is shown. The pressure of the conveying hole 9 after the blade 4, that is, the pressure of the blade separated by the blade from the outlet hole of the pump is less than or equal to the pressure of the outlet hole 7, and the elastic element 47 of the blade 4 is applied to the wall of the blade chamber 3. It is acted on by the force which pressurizes. The pressure of the conveying hole 9 after the blade 4 starts to exceed the pressure of the outlet hole 7, and the elastic element 47 of the blade 4 is pushed in from the wall of the blade chamber 3 to bend by opening the conveying hole 9 (this embodiment). The hydraulic motor mode for accords with the opposite sign of pressure drop in the opposite direction of rotor rotation).

Separation angle φ delivery of the conveyance hole from the conveyance hole _. In order to carry out the method of adjusting the overall angle by changing the above, the present invention provides two embodiments of the means for deforming the overall angle. In the first embodiment (FIG. 27), the overall angle adjustment valve 43 is formed in the front limit bypass path 44 of the stator unit, one end of the path 44 communicates with the inlet hole 6, and the other end of the path 44. The part has the possibility of being connected to the transport hole 9 and enters the forward transport area. The valve 43 is formed with the possibility of closing the path 44 at a rotor rotation angle equal to the separation angle. In a preferred embodiment, the valve is formed by an electric drive source that is electrically connected to a detector of the magnitude and phase of the pressure oscillations in the outlet hole. The use of an adjustment valve with an overall angle that can be electrically opened and closed during the period set for each conveying hole is due to the pressure drop and the rotational speed of the rotor _. Provide maximum flexibility for adjustment. However, such valves are opened and closed many times during one rotation of the rotor, and the operating speed of such valves limits the possibility of adjusting the separation angle due to the high speed rotation of the rotor. In order to adjust the separation angle with the high speed rotation of the rotor, the present invention provides various fronts formed in the housing of the device (eg of a forward transport limiter) with the possibility of a hydraulic connection to the transport holes. The whole angle adjustment valve is used in the form of a sliding valve selector with a restricted bypass path. Each bypass path is hydraulically connected to a selector switch that is hydraulically connected to the inlet hole. The rotational angle of the rotor, in which the different bypass paths are separated from the current conveying hole by means of rotary insulation, for example vanes, corresponds to the different angles of separation of this conveying hole from the inlet hole. The bypass path that is hydraulically connected to the inlet hole via the selector is selected according to the pressure difference and the rotational speed of the rotor. Thereby, one separation angle is selected from a set of separation angles. The selector switch can be formed, for example, as a solenoid distribution valve that is electrically connected to a detector of the magnitude and phase of the pressure oscillation in the outlet hole. A cost-effective embodiment of the present invention that adjusts the separation angle by the pressure difference (FIG. 28) is a piston 49 that is influenced by the fluid from one side under the outlet pressure and from the other side under the pressure close to the inlet. The embodiment of the selector as a piston valve selector 48 with a proof spring 50 is tolerated. The position of the piston is determined by the balance between the compression force and the calibrated spring elastic force, changing the set of bypass paths 44 connected to the inlet holes 6 and thereby changing the separation angle.

φ _DETCH. In a second embodiment of the overall angle changing means for adjusting the angle, the present invention provides a blade drive mechanism comprising means for changing the separation angle of the conveying hole from the inlet hole by the blade. Separation angle _φdeatch. The blade drive mechanism that can change the angle is formed, for example, as a cam mechanism including a carrier 51 attached to the housing 1 of the guide groove 52 on which the side protrusion 53 of the blade 4 slides. The shape of the groove determines the movement characteristics of the blade in the axial direction by the rotation of the rotor. The blade drive mechanism controls the periodic movement of the blade 4 with respect to the operating part 2 of the rotor by its rotation, and the blade 4 in the suction area A moves axially from the blade chamber 3 to the annular groove 23, and in the forward conveyance area B. The cross section of the working chamber that separates the transport hole from the inlet hole is cut off. A person skilled in the art understands that the separation angle of the conveying hole 9 from the inlet hole 6 by the blade 4 is changed by the rotation of the carrier 51 around the rotation axis of the rotor. The means for changing the separation angle for such a blade drive mechanism uses, for example, an electric drive source of the carrier 51 that rotates in electrical connection with a detector of magnitude and phase of pressure oscillations at the outlet hole. Can be executed.

  In order to implement the overall angle adjustment method described above with respect to the rear transport hole, the present invention provides at least one rear surface in sliding insulation contact with the rear transport limiter and connected from the inlet and outlet holes to at least one forced chamber of variable capacity. A rear conveying insulated rotor means for separating the conveying holes is supplied. In this case, each rear transfer hole coincides with its respective range of rotor rotation angles from which the rear transfer hole is separated from the inlet and outlet holes, and the apparatus includes a total angle adjustment valve for rear transfer. At least one rear restriction bypass path is provided. One end of the rear restriction bypass path is connected to the inlet hole, and the other end of the path enters the rear transport area with the possibility of being connected to the rear transport hole. The valve is formed with the possibility of opening the rear restriction bypass path when the pressure drop sign between the two ends of the rear restriction bypass path changes.

  The rear conveying insulation rotating means comprises a portion of the inner cylindrical surface of the annular groove that is in sliding insulation contact with the rear conveying limiter. In one embodiment, the insulating means comprises a portion of the blade surface that is in sliding insulation contact with the rear transport limiter. In a preferred embodiment, the insulating means comprises a point on the bottom surface of an annular groove 64 (FIGS. 29 and 30) in sliding contact with the rear transport limiter 22.

Detailed description of the apparatus and operation of an embodiment of the proposed invention In order to explain the design and operation of an embodiment of the proposed invention in detail, a rotor suitable for reducing friction loss is preferred. A variation of a configuration that tends to be calibrated at high speeds and is intended to be used as a pump will be described.

  The device of the embodiment of the present invention (FIGS. 22, 29-34) comprises two main units: a housing and a rotor that is mounted in the housing with the possibility of rotation.

  The rotor has the possibility of axial movement of the actuating part 2 with the vane chamber 3, the annular groove 23 of constant rectangular cross section formed on the actuating surface, and the vane chamber 3 connected to the annular groove 23. And a blade 4 having a path 46 to be installed.

  The housing 1 is formed by an inlet 24 and an outlet 25, and a support cover plate 30 composed of a surface working cover plate 21, a load bearing element 54, and an internal functional element, and an undeformed chamber 56 connected to the outlet hole 25 is A suction distribution hole 57 and a pressure distribution hole 58 formed between the load bearing and the functional element and divided by the insulating dam 59 are formed in the functional element of the support cover plate.

  The working chamber of the device is radially coupled by the inner surface of the annular groove 23 and is axially coupled by the inner surface of the working cover plate 21 of the housing 1 and the bottom surface 60 of the annular groove 23. In order to consider the processing of the apparatus during the transfer of the working fluid, four areas, a suction area A, a front transfer area B, a pumping area C, and a rear transfer area D are planned (FIG. 30).

  The suction area A of the working chamber corresponds to the position of the inlet hole (or suction hole) connected to the inlet 24, and the pressure feeding area C of the working chamber matches the position of the outlet hole (pressure feeding hole) connected to the outlet 25. Accordingly, the connection of the inlet and outlet holes to the inlet and outlet is formed in the housing cover plate 21 via paths 61 and 62, but in other embodiments of the invention the path of the rotor is routed. It can also be formed via.

  The forward transfer area B is arranged between the suction area A and the pressure-feed area C of the working chamber. In this region, the fluid contained in the working chamber between the blades 4 and the rotor hole connected to the working chamber is transported from the suction region A to the pressure feeding region C. In the rear conveyance area D, the fluid portion from the pressure feeding area C is returned to the suction area A and conveyed.

  The front transfer limiter 5 is attached to the operation cover plate of the housing, is disposed in the operation chamber of the front transfer area B, and is in sliding contact with the sealing material 45 of the blade 4 protruding in the annular groove 23. Thereby, the possibility of separating at least one transport hole 9 from the inlet hole 6 and the outlet hole 7 by means of a blade is provided. The transport hole 9 is coupled to the annular groove by the surface of the front transport limiter and two adjacent blades. Each of the transport holes has an individual range of rotor rotation angles at which the transport holes are separated from the inlet and outlet holes.

  The limiter 5 is formed to be movable in the axial direction. In the case of the movement in the axial direction, the cross-sectional area of the front conveyance area changes, and therefore the movement of the apparatus also changes. In order to control the movement in the axial direction, the apparatus has a drive mechanism for a forward conveyance limiter. In a stable moving device, the forward transport limiter can be formed as a flat insulating dam on the working cover plate of the housing.

  The blade drive mechanism 63 is formed as a cam mechanism including a carrier 51 attached to the housing 1 of the guide groove 52 in which the side protrusion 53 of the blade 4 slides. The shape of the groove determines the operating characteristics of the blade in the axial direction with the rotation of the rotor. The blade driving mechanism controls the periodic movement of the blade 4 with respect to the operating part 2 of the rotor by the rotation thereof, and the blade 4 in the suction region A moves in the axial direction from the blade chamber 3 to the annular groove 23, and forward transport region B Then, the cross section of the working chamber is cut off, and in the pressure feeding area C, the section moves from the annular groove 23 to the blade chamber 3, and in the rear transfer area D, the cross section of the working chamber is opened.

  The forward conveyance limiter driving mechanism described above is kinematically connected to the blade driving mechanism, and when the position of the forward conveyance limiter with respect to the bottom surface of the annular groove changes, the size of the protrusion of the blade into the annular groove in the forward conveyance region also changes. The sliding insulation contact of the blade sealing material with the forward conveying limiter can be maintained.

  Other embodiments of the present invention have different characteristics of blade movement. The moving characteristic of the blade with respect to the rotor that periodically changes the range of blocking the cross section of the annular groove by the blade is allowed. For example, with the exception of the design of axial movement, there are also radial rotational movements of the vanes and combinations thereof. Regardless of the changeable pump's blade movement characteristics, the mechanism changes the size of the blade's protrusion from the blade chamber to the annular groove in response to a change in the cross-sectional area of the working chamber in the forward transfer area Therefore, it is kinematically connected to a forward transfer limiter that is movable in the axial direction.

  The rear conveyance limiter 22 is attached to the operation cover plate 21 of the housing, is disposed in the operation chamber of the rear conveyance area D, and is in sliding insulation contact with the rear conveyance insulation rotating means including the inner surface of the annular groove 23 and the bottom surface sealing material 64. This gives the possibility of separating at least one rear transport hole 66 limited by the surface of the rear transport limiter 22 and two adjacent bottom seals 64, with the forced chamber 10 from the inlet hole 6 and the outlet hole 7. Yes. Each of the rear transport holes has an individual range of rotor rotation angles at which the rear transport holes 66 are separated from the inlet hole 6 and the outlet hole 7.

  In another embodiment of the invention, the rear transport limiter 22 is in sliding insulation contact with the vanes, which are formed to be movable in the axial direction. That movement changes the movement of the device. In this case, the blade drive mechanism is kinematically connected to an axially movable rear conveyance limiter, and in response to a change in the cross-sectional area of the working chamber in the rear conveyance region, Change the range.

  Moreover, in this embodiment, the rotor includes a support portion 13 having a support hole 32 formed in the outer surface thereof. The support holes are insulated by a flat surface of the insulating dam 31 and a sealing 67 on the peripheral surface by active insulating contact between the flat insulating surface of the support cover plate 30 of the housing and the flat surface.

  The working part and supporting part of the rotor are correspondingly attached to the housing working cover plate 21 and support cover plate 30 with bearings 68 and connected to the inlet shaft 69 by joints, which rotate simultaneously but in the axial direction. Do not move and tilt relative to each other.

  The rotor also has a variable capacity forcing chamber disposed between the working part 2 of the rotor and the support part 13 of the rotor. The forcing chamber of the embodiment of the device is mounted with a forcing hole 70 formed in the surfaces of the rotor actuating part 2 and the support part 13 facing each other and with the possibility of sliding in the forcing hole. It is formed by a tubular connector 71. The tubular connector has a sealed shoulder. Their shape, position and dimensions are selected to insulate the forcing chamber within the entire range of axial movement and to tilt the support part of the rotor relative to the working part of the rotor.

  The forcing chamber 70 of the rotor support portion 13 is connected to the support hole 32 via a path 72. The forcing hole 70 in the working part of the rotor of the device according to the embodiment of the invention is formed as an enlargement of the vane chamber 3 and is connected to the working chamber via the vane path 46. The forced chamber has a spring 73 that seals when there is no pressure.

  The tilting means of the rotating shaft of the supporting portion of the rotor with respect to the rotating shaft of the operating portion of the rotor of the apparatus according to the embodiment of the present invention includes the support cover plate 30 of the housing and the tilting shaft 36 fixed to the housing 1. And means for tilting the support cover plates of the housings of those rotations holding the support cover plates 30 of the housings with the possibility of rotation. They also include a housing limiting thrust 74, a housing fixed thrust 75, a spring 76, and a tilt angle changer of the housing support cover plate relative to the housing operating cover plate. The inclined shaft 36 is disposed so that the moment of the compressive force of the working fluid acting on the support cover plate 30 of the housing from the support portion 13 side of the rotor is minimized. The housing limiting thrust 74 is formed so that it can limit the tilt angle of the housing support cover plate. The fixed thrust 75 of the housing is formed so that the axis of rotation of the support portion 23 of the rotor and the rotation axis of the operating portion can be made parallel by adjoining the fixed thrust 75 of the housing of the support cover plate 30 of the housing. The spring 76 fixes the support cover plate of the housing to the fixed thrust of the housing with zero pumping pressure. The tilt angle changer comprises a housing adjustment thrust 77, a mode switching valve 78, and a control valve 18, where the converter of the difference between the reference pressure and the pressure at the rotor rotation angle is the reference to movement. Equal to an angle. The converter is formed in the form of a differential double-acting hydraulic cylinder 15 that is attached to a support cover plate 30. The first hole of the hydraulic cylinder 15 is hydraulically connected to either the control valve 18 or the outlet hole 17 via a mode switching valve 78. The control valve 18 is hydraulically connected to a control path 79 formed in the support cover plate 30 of the housing, and one end of the control valve 18 enters the surface of the insulating dam 59 to support the support portion of the rotor 13 in the forward transfer region. 32 is communicated. The second hole of the hydraulic cylinder 15 is hydraulically connected to either the braking path 80 or the inlet hole 6 via a mode switching valve 78. The braking path 80 is hydraulically connected to the undeformed chamber 56 of the housing support cover plate 30 connected to the outlet hole 7. The area of the piston facing the first hole 16 is equal to S1, the area of the piston facing the second hole 17 is equal to S2, and S2 <S1 (S2 = 0.0 in the apparatus of the embodiment of the present invention). 5 · S1). The rod 81 of the piston 14 is placed on the housing adjusting thrust 77 via a sliding element 88 adjacent to the surface by inclination. The mode switching valve 78 and the control valve 18 are electrically connected to a converter 82 for magnitude and phase of vibration to shift angle. The transducer includes a sensor 83 electrically connected to the rotation angle of the rotor, a fast response pressure vibration sensor 84, and a microcontroller 85 having a timer and a digital amplitude converter.

  The angle of the outlet hole of the apparatus according to the embodiment of the invention is selected so that the moment of separation of the current rear conveying hole from the outlet hole by the vanes coincides with the moment of merging with one of the outlet holes of the conveying hole. . Therefore, in order to compensate for the second kinematic non-uniformity of the delivery to the outlet hole, the apparatus considered was provided with one compensatory path 19 and a compensatory slip valve selector. The compensatory slip valve selector of the apparatus according to the embodiment of the present invention is formed as a distribution path 41 formed in the forward conveying limiter 5 while blocking the blades 4 by rotation of the rotor. The distribution path 41 is connected to a compensatory path 19 which includes a variable hydraulic resistance compensating throttle 42. The means for changing the hydraulic resistance of the compensation throttle 42 is not shown in the drawing.

  The rear conveyance limiter 22 has a rear restriction bypass path 86 including an entire angle adjustment valve for rear conveyance, and one end portion of the rear restriction bypass path 86 is connected to the inlet hole 6, and the other end portion of the path 86. Communicates with one of the rear conveying holes 66, and the valve can open the rear pressure limiting bypass path 96 when the pressure drop sign between the two ends of the rear pressure limiting bypass path 86 is changed. It is formed with properties.

  Consider the implementation of the method described above in the action of the device in pump mode and the pressure changes in the transport and rear transport holes. Suppose that by starting to consider the outlet pressure of the pump outlet, i.e. the pumping hole, the pressure of the pump inlet hole, i.e. the suction hole, is significantly exceeded. To consider a complete cycle consisting of suction, forward transfer, pumping and reverse transfer, the state of the working fluid in the holes connected by the movement of one selected blade to the blade chamber is followed. The first moment coincides with the selected blade position at the beginning of the suction area. The pump operates as follows.

  At the first moment of the cycle equal to one rotation of the rotor, the selected blade 4 is located at the boundary between the rear transfer area and the suction area.

  When the inlet shaft 69 is rotating, torque is conveyed to the working part 2 and support part 13 of the rotor via the joint 87 and rotates relative to the housing 1.

  In the rotation of the rotor, the lateral projection 53 of the blade 4 slides along a guide groove 52 shaped such that the blade moves from the blade chamber 3 in the suction area A to the annular groove 23. At the same time, the working fluid fills the space of the blade chamber 3 evacuated by the moving blade 4 via this blade path 46. In addition, the fluid flows into the blade chamber 3 of the selected blade via the other blades, the suction distribution holes 57, the support holes 37, the paths 72 and the path 46 of the forced chamber 10 which reduces the tendency of the pump for calibration. I can enter.

  While the working fluid in the forced chamber is at low pressure or zero pressure, the forced hole in the forced chamber is pulled separately by the spring 73. The protruding blades in the front conveyance region B are in sliding contact with the front conveyance limiter 5 by the sealing material 45, and the inner blade hole 8 blocked by the sealing material of the previous blade 4 in front of the rotation direction of the rotor from the inlet hole. To separate. The insulating dam 31 in the support portion of the rotor in the front transfer region is in sliding contact with the insulating dam 59 in the support cover plate of the housing, and the support hole 32 blocked by the previous dam in the front in the rotation direction of the rotor is divided into the distribution hole and Separate from the inlet hole. Current conveying part of the working fluid limited to the capacity of the inner vane hole 8, the path of the vane 46, the vane chamber 3, the forced chamber 10, the path 72 and the support of the support part 13 of the rotor that jointly form the conveying hole 9 The hole 32 is closed in the forward conveyance area.

  In the rotation of the rotor, the transfer portion of the working fluid moves from the inlet hole 6 to the outlet hole 7 through the transfer hole 9.

  The inclination angle of the rotating shaft of the support portion of the rotor 13 with respect to the rotating shaft of the operating portion of the rotor 2 is determined by the position of the piston 14 of the differential double-acting hydraulic motor 15. In the operating mode, i.e., when the vibration is caused only by the decompression flow, the first hole 16 of the hydraulic cylinder 15 is connected to the control valve 18 via the mode switching valve 78 when there is no vibration change or vibration leakage of the load. The second hole 17 is connected to the outlet hole via the mode switching valve 78 and the braking path 80. Due to the presence of the reduced pressure flow, the capacity of the braking path 80 and the second hole 17 smoothes out the pressure oscillations in the outlet hole 7, so that the pressure in the second hole 17 of the hydraulic motor 15 is equal to the capacity of the second hole 17. The time determined by the hydraulic resistance of the braking path 80 is equal to the averaged outlet hole 7 pressure. The piston 14 has the above-described moment of the compressive force of the working fluid acting on the support cover plate 30 of the housing from the side of the support portion 13 of the rotor due to the force that the difference in compressive force acting on the piston is connected to the elasticity of the spring 76. Take a position to balance with.

  If the pressure vibration characteristic of the outlet hole shows a vibration change of the load or a large value of vibration leakage due to the destruction of the pump, that is, if there is a structure with a large amplitude of the vibration spectrum of the frequency below the frequency of the decompression vibration The first hole 16 is connected to the outlet hole 7 via a mode switching valve 78, and the second hole 17 of the hydraulic motor 15 is connected to the inlet hole via a mode switching valve 78 to support the housing support cover plate. 30 occurrence of vibration is prevented. In this case, the piston 14 is in the first position until the support cover plate is adjacent to the fixed thrust of the housing 75 and the rotational axis of the support part 13 of the rotor is parallel to the rotational axis of the working part 2 of the rotor. The first hole 16 moves to the second hole 17.

  In the movement of the transfer part, the capacity of the forced chamber 10 decreases according to the sinusoid law due to the inclination of the rotation axis of the support part 13 of the rotor. The tilt angle is selected so that the density and pressure of the working fluid in the forced chamber increase at the current level of change in the working fluid volume in the transfer hole caused by the leakage rate and the rotational speed of the rotor.

All for forming a transport hole 92 that restricts the selected transport portion of the working fluid for the local pressure balancing means as a collection of the vane 4 passage 46, the rotor support portion passage 72 and the tubular connector 71 passage. Changes in pressure in the holes 8, 46, 3, 10, 72, 32 of
The reference angle at which the conveying hole is connected to the hole 16 of the hydraulic cylinder 15 via the control valve 18 is determined by a shift angle that is different from the rotation angle of the rotor at which the selected conveying hole joins the outlet hole and the reference angle. A signal that opens and closes the control valve 18 and thereby determines the shift angle is generated by a phase and amplitude converter 82 of the outlet pressure oscillation to shift angle. The microcontroller 85 of the converter 82 reads signals from the rotation angle sensor 83 and the pressure vibration sensor 84 of the rotor, and the moment corresponding to the rotation speed of the rotor, the merge with the outlet hole of the conveying hole, and the pressure for the moment of the merge. Calculate the vibration amplitudes and their phases and the closing characteristics, i.e. the shift angle, the reference angle or the corresponding moment when the control valve 18 receives the opening and closing signal. In the stationary region, the magnitude of vibration does not exceed the set acceptable level and the transducer does not change the current open characteristics. In the area parameter, when the vibration phase matches the overall excessive magnitude of the change in the capacity of the transport hole, when the vibration phase matches the insufficient overall magnitude, for example, load, pump movement, The leakage rate or rotor rotation speed is changed prior to the magnitude of vibration above the level, and the transducer changes the opening characteristics, i.e. reduces the shift angle. When the rotational speed of the rotor is changed, the converter changes the opening / closing interval of the control valve.

  When the rotor is equal to the opening angle of the valve 18 at the selected reference value for the selected conveying hole, the converter 82 generates an opening signal which becomes the opening control path 79 by the control valve 18 and differentially The transfer hole 9 is connected to the first hole 16 of the double-acting hydraulic cylinder 15.

  If the pressure in the transport portion is less than or equal to the pressure in the first hole 16 of the hydraulic cylinder 15, a compensatory relative flow from the hydraulic cylinder 15 to the transport hole 9 occurs via the control path 79, and the working fluid in the transport portion 15 Increase volume. The pressure in the conveying portion increases and the pressure in the first hole 16 of the hydraulic cylinder 15 decreases. The piston 14 of the hydraulic cylinder moves from the second hole 17 to the first hole 16 to increase the overall change in the tilt angle of the rotation shaft of the support portion of the rotor 13 and the capacity of the transfer hole. .

  If the pressure in the conveying part exceeds the pressure in the first hole 16 of the hydraulic cylinder 15, a compensatory relative flow from the hydraulic cylinder 15 to the conveying hole 9 occurs via the control path 79, and the working fluid Reduce the volume. The pressure in the conveying portion decreases and the pressure in the first hole 16 of the hydraulic cylinder 15 increases. The piston 14 of the hydraulic cylinder moves from the first hole 16 to the second hole 17 to reduce the overall magnitude of the change in the tilt angle of the rotating shaft of the support portion 13 of the rotor and the capacity of the transfer hole. .

  When the pressure in the conveying part is equal to the pressure in the first hole of the differential double acting hydraulic cylinder, no working fluid flows between them and the piston does not operate.

  In the rotation of the rotor at an angle corresponding to the moment of merging with the exit hole of the previous transport hole, the blade separating the selected transport hole from the previous one is a compensatory slip connected to the compensatory path 19 Ends the blockage of the valve selector distribution path. As a result, a compensatory flow of the working fluid from the outlet hole to the conveying hole 9 occurs. At the moment of occurrence, the compensatory flow has a maximum rate when the pressure difference between the inlet hole and the transfer hole at this moment is maximized. The pressure in the conveying part is increased by reducing the capacity of the conveying hole by reducing the capacity of the forced chamber and by reducing the volume of working fluid in the conveying part by compensatory flow. At the same time, the rate of compensatory flow decreases. In the stationary region, the pressure of the transport portion becomes equal to the pressure of the outlet hole 7 due to the moment of merging with the outlet hole of the transport hole. Thus, the compensatory flow rate is reduced to zero by this moment.

  The previous blade 4 moves from the front transport limiter 5 at the end of movement of the selected transport portion to the exit hole in the front transport area. There, the insulating dam 31 of the support hole 32 of the selected transfer capacity moves from the insulating dam 59 to the area of the pressure distribution hole 58 of the support cover plate 30 of the housing. Thereby, the selected conveyance hole merges with the pressure feeding hole. The pressures of these working fluids are equalized, and no decompression flow occurs between them at the moment of merging. As a result, the flow of working fluid to the outlet hole and pressure line is characterized by the absence of pressure oscillations.

  At the same instant, the phase and amplitude converter 82 of the outlet pressure oscillation to shift angle captures the outlet hole pressure. When there is no reduced pressure flow or pressure vibration caused by them at the outlet holes, the amplitude of the vibrations taken by the transducer does not exceed a predetermined tolerance level and the transducer does not change the current opening characteristics.

  When one of the characteristics, such as load, rotational speed, movement or leakage rate, changes substantially, a reduced pressure flow and corresponding pressure vibration occurs in the pumping hole and the amplitude of the vibration exceeds the level. In this case, when the amplitude of vibration coincides with the excessive overall change in the capacity of the transport hole, that is, a reduced pressure flow is generated from the transport hole to the pumping hole, and the pumping at the moment of merging with the outlet hole of the transport hole is performed. If the hole pressure increases step by step (curve 8 in FIG. 2), the transducer decreases the shift angle. However, if the phase of vibration coincides with the overall size of the change in capacity insufficient, that is, if the pressure at the pumping hole at the moment of merging decreases step by step (curve 7 in FIG. 2), the conversion The instrument increases the shift angle.

  Transducer 82 differs differently when non-uniform wear causes different rates of leakage through the insulating surfaces of different transport holes, and different exit holes generate reduced flow direction and value at the confluence of different transport holes. Change the shift angle for the transport hole. The converter 82 reduces the shift angle with respect to the average shift angle because of the hole that, due to the confluence with the pumping hole, causes a depressurization flow towards the subsequent pumping hole due to a distinct jump in outlet pressure. As a result, when the pressure in the transport portion exceeds the pressure in the first hole 16 of the hydraulic cylinder 15, the control valve 18 is opened and the transport hole merges with the first hole 16 in the hydraulic cylinder 15 at a later point. . Compensatory and relative flow occurs from the transfer hole to the first hole 16 of the hydraulic cylinder 15, reducing the volume of working fluid in this transfer portion and reducing the vacuum flow, and reducing the flow between the transfer hole and the outlet hole. This creates a clear pressure jump at the confluence. The transducer increases the shift angle relative to the average shift angle because of the hole that generates a reduced flow directed from the pumping hole following a conservative jump in outlet pressure by confluence with the pumping hole. As a result, when the pressure in the conveying portion is equal to or lower than the pressure in the first hole 16 of the hydraulic cylinder 25, the control valve 18 is opened, and the conveying hole joins the first hole 16 in the hydraulic cylinder 15 at an early point. Compensatory and relative flow occurs from the first hole 16 of the hydraulic cylinder 15 to the transfer hole 9, increasing the volume of working fluid in this transfer portion and reducing the reduced pressure flow, This creates a modest pressure jump at the confluence.

  A non-uniform change in load or partial destruction of the elements of the pump produces an oscillation of the outlet pressure with a large amplitude and a frequency much less than the frequency of the decompression oscillation at this rotational speed of the rotor, after which the transducer 82 Assigns a switching signal to the mode switching valve 78. In this case, the first hole 16 of the hydraulic cylinder 15 is connected to the outlet hole 7 and the second hole 17 of the hydraulic cylinder 15 is connected to the inlet hole. At the same time, the piston 14 is in the first position until the support cover plate is adjacent to the fixed thrust of the housing 75 and the rotational axis of the support part 13 of the rotor is parallel to the rotational axis of the working part 2 of the rotor. It moves from the hole 16 to the second hole 17.

  The sinusoidal change in the capacity of the forced chamber due to the merge of the transport hole 9 with the pressure feed hole 7 causes a first type of discharge jump from the transport hole to the exit hole. As described above, the configuration of the outlet hole that joins the conveying hole with the outlet hole coincides with the moment when one of the rear conveying holes 66 is separated from the outlet hole. Therefore, the second type discharge jump is added to the first type discharge jump that increases its magnitude. However, the compensatory flow from the exit hole to the next transport hole via the compensatory path 19 occurs at the same moment. The compensatory throttle 42 resistance is selected so that the compensatory flow rate at this moment is equal to the value of the discharge jump from the forced chamber 10 to the outlet hole 7. Thereby, all working fluid moved from the forced chamber 10 is drawn into the compensatory path 19. As a result, an undulating flow of working fluid occurs at the outlet 25 of the pump.

  If the rotational speed of the rotor or the movement of the pump is changed, the means for changing the hydraulic resistance of the compensatory path 19 will change the hydraulic resistance of the compensatory throttle 42. Then, if the rotor speed or pump movement increases, the means will reduce the compensatory throttle 42 resistance, and if the rotor speed or pump movement decreases, the means will be compensatory. The resistance of the throttle 42 is increased.

  When the selected blade passes through the pumping area, the side projection of the blade moves the blade in the pumping area C from the annular groove 23 to the blade chamber 3 and moves the working fluid to the outlet hole 7 via the path 46. It slides along the guide groove 52 of such a type.

  When the selected vane passes, the pumping area C with the first sinusoidal change of the capacity of the forced chamber 10 gradually reduces the transport of this forced chamber to the outlet hole 7 and then the sign of said transport And gradually reduce the suction from the exit hole into the forced chamber. Several forced chambers move simultaneously in the pumping area. Some of them move the working fluid to the pumping holes and some are drawn from the pumping area into the working area. The overall transport of all these forced chambers determines the characteristics of the second kinematic non-uniformity of the transport to the pumping holes (curve 35 in FIG. 17) and is gradually reduced with increasing transport steps. The aforementioned compensatory flow reduction characteristic (curve 33a in FIG. 16) is close to the transport characteristic from the forced chamber. Thus, in practice, all the working fluid moved from the forced chamber is drawn into the compensatory path and the undulating flow of working fluid (curve 36 in FIG. 17) is not only during the jump but also during the jump. It occurs at the outlet of the pump.

  By the moment when the selected blade approaches the rear transfer area D (FIG. 30), it completely enters the blade chamber. The bottom sealing material 64 of the annular groove 23 that moves close to the blades selected from both sides with respect to the rotation direction of the rotor and moves from the pumping area to the rear conveyance area is in active insulating contact with the surface of the rear conveyance limiter. The bottom hole 65 is closed. The insulating dam 31 of the support portion 13 of the rotor in the rear transfer area is in sliding contact with the flat insulating dam 59 of the support cover plate of the housing and closes the support hole 32 from the rear. From the front, the support hole 32 is closed by the previous insulating dam 31. Thereby, in the rear transfer region, the current rear transfer portion of the working fluid is the rear transfer hole 66 including the capacity of the bottom unloading hole 65, the path of the blade 4, the blade chamber 3, the forced chamber 10, and the support portion 13 of the rotor. The path 72 and the support hole 32 are closed. Then, suction from the exit hole into the forced chamber leads to a clear jump of the second type of transport into the exit hole and stops. Due to the configuration of the outlet hole 7 described above, the separation of the rear conveying hole from the outlet hole coincides with the moment when one of the conveying holes merges with the outlet hole. Therefore, the second type of discharge jump is added to the first type of discharge jump that increases its size. When the total discharge jump is fully compensated by the compensatory flow as described above, a highly uniform flow of working fluid in the pump outlet duct is achieved.

  In the rotation of the rotor, the rear conveying hole 66 moves from the outlet hole 7 to the inlet hole 6.

  Due to the inclination of the rotation axis of the support part of the rotor, the capacity of the forced chamber of the variable capacity 10 increases according to the sinusoidal law by the movement of the rear transfer hole, and thus the density and pressure of the working fluid in the forced chamber increase its capacity. Sometimes reduced. In expanding and increasing the capacity of the forced chamber 10, the working fluid does a useful job to partially compensate for the consumed work of the compression of the working fluid in the transport holes.

  The pressures of all the holes 65, 46, 3, 10, 72, 32 forming the rear conveying holes by the local pressure means balanced as the set of paths of the blades 4, the rotor support part path 72 and the tubular connector 71. Change is equal.

  In the described variable movement pump, the angle of the rear conveyance area D is selected to be equal to the angle of the front conveyance area B, and the capacity of the conveyance hole at the junction with the pressure feeding hole is the rear conveyance hole at the moment of separation from the pressure feeding area. An inlet pressure level that reduces the movement of the pump to zero when it is equal to the capacity of the rear is provided with an enlargement range of the rear conveying hole sufficient to reduce the pressure in the rear conveying portion. Therefore, when the movement of the pump is increased, the rotational angle range of the rotor in which the rear conveyance hole is separated from the outlet hole and the inlet hole is reduced by the early connection with the inlet hole of the rear conveyance hole, and the end of the rear restriction bypass path 86 is reduced. The valve 43 is opened at the sign of the pressure drop between the parts, and the working fluid is increased in capacity by the further movement of the rear transfer hole 66 until the moment of merging with the suction hole 6. Sucked from. Thereby, an excessive change in the pressure of the rear conveying hole that can lead to pressure reduction or calibration is prevented, and the working fluid is uniformly generated in the suction line of the pump.

  The operation of the above-described apparatus is based on the proposed method for generating an undulating flow of working fluid, and the apparatus for implementing the same eliminates the occurrence of decompression vibration, and the second kinematics of the conveyance. It compensates for non-uniformity, generates a uniform working fluid flow at a high level, and overcomes the significant disadvantages of fluid power drive sources such as vibration and noise and corresponding power losses.

Inlet hole _φdeatch. From its separation angle from the outlet hole φ _merg. Is a chart of the change in the capacity of the conveying hole and the pressure of the working fluid at a constant mass of the conveying part of the working fluid, due to each movement φ of the conveying hole within the range to its merging angle. It is a chart of the wave of the outlet pressure generated by the decompression flow and the compensation flow at the confluence of the conveying hole and the outlet hole when there is no leakage. It is the schematic which performs the change method of the capacity | capacitance of the conveyance hole of the rotor sliding blade apparatus which has a variable length forced chamber, and is a fracture | rupture figure of the cyclic | annular expansion | deployment of a front conveyance area | region. It is the schematic which performs the change method of the capacity | capacitance of the conveyance hole of the rotor sliding blade apparatus which has a support part of a rotor which has a variable length forced chamber, and is a fracture | rupture figure of the cyclic | annular expansion | deployment of a front conveyance area | region. _{Φdeatch in} adjusting the overall magnitude of the change in the capacity of the transport hole by the outlet pressure in the absence of leakage and compensation flow _. To φ _merg. It is a chart of the change of the capacity | capacitance of a conveyance hole by the angle movement of the conveyance hole in the range, and the pressure of the working fluid. FIG. 6 is a schematic diagram for adjusting the overall magnitude of the change in capacity of the transport hole by the difference between the reference pressure at the reference angle and the pressure of the transport hole using a differential double-acting hydraulic cylinder and a control valve. _{Φdeatch in} adjusting the overall magnitude of the change in capacity of the transport hole due to the difference between the reference pressure at the reference angle and the pressure of the transport hole _. To φ _merg. It is a chart of the change of the compensatory comparative flow rate ratio and the conveyance hole by the angle movement of the conveyance hole in the range of, and the change of the mass and pressure of the working fluid. Change in the capacity of the transport hole, _φdeatch. To φ _merg. 6 is a chart of changes in the mass and pressure of the working fluid due to the annular movement of the transport hole within the range, and shows changes in the shift angle and the reference angle when the leakage rate from the transport hole changes. _Merge angle φ _{merg. Φdetach in} the adjustment of the overall angle that changes the pressure of the working fluid due to the outlet pressure due to the change of _. To φ _merg. It is a graph of the flow rate ratio of the fluid between the conveyance hole and an exit hole, and the change of the mass and pressure of a working fluid by the cyclic | annular movement of the conveyance hole in the range. Separation angle _φdeatch. Φ adjustment in the adjustment of the overall angle that changes the pressure of the working fluid in the conveying hole due to the outlet pressure due to the change in the _. To φ _merg. FIG. 6 is a chart of a change in mass and pressure of a differential fluid due to an angular movement of a transport hole within the range of and a fluid flow rate ratio between the transport hole and the inlet hole. FIG. 6 is a diagram of a second kinematic non-uniformity of the transport caused by a sinusoidal wave of the capacity of the transport hole (the first and second types of transport surges do not drop at the same time interval). FIG. 6 is a diagram of a second kinematic non-uniformity of the conveyance caused by a sinusoidal wave of the capacity of the conveying hole (the first and second types of rapid increase in conveyance fall at the same time interval). FIG. 6 is a chart of the wave of the outlet pressure caused by the reduced pressure caused by the kinematic non-uniformity of the transport at zero capacity of the outlet duct and the wave of the second outlet pressure. FIG. 6 is a diagram of a second outlet pressure wave caused by a second kinematic non-uniformity of conveyance at a small capacity of the outlet duct. FIG. 6 is a schematic diagram of a second kinematic non-uniform compensation method of transport using a compensating hydraulic duct between the outlet hole and the nearest transport hole. A diagram of the change in capacity of the transport hole, its differential fluid mass and pressure, and _{φdeatch in} the generation of a compensation flow between the exit hole and the nearest transport hole _. To φ _merg. The flow rate ratio is compensated by the angular movement of the transport hole within the range of FIG. 5 is a diagram of the remaining second kinematic non-uniformity of the transport when there is a compensating flow between the exit hole and the transport hole separated from the exit hole by one vane. FIG. 6 is a diagram of a second wave of outlet pressure when there is a compensating flow between a transport hole separated from the outlet vane by one vane due to the zero capacity of the outlet hole and outlet duct. FIG. 6 is a schematic diagram of a second kinematic non-uniformity compensation method for transport using a compensating hydraulic duct between the transport hole separated from the exit hole by an exit hole and two vanes. Φdeatch in the change in the capacity of the conveying hole, the generation of a compensation flow between the outlet hole and the conveying hole separated from the outlet hole by at least two blades _. To φ _merg. It is a graph of the change of the mass and pressure of the working fluid by the angular movement of the conveyance hole in the range of, and the change of the compensation flow rate ratio. Rotor sliding vane device having a variable capacity forced chamber between the working part of the rotor and the support part of the rotor supported by a rotary thrust in the form of a rotary bearing, passing through the bearing rear and forward transport limiters It is sectional drawing along the plane which passes along the plane which passes, and the plane which passes an inlet_port | entrance and an exit. A rotor sliding vane device having a variable volume forcing chamber between a working part of the rotor and a support part of the rotor that is active along the support cover plate of the housing, along a plane passing through the inlet and outlet FIG. Variable capacity rotation between the rotor support part and the rotor coupling element, with a housing operation and support cover plate joined to the housing operating unit located between the rotor actuating part and the support part FIG. 2 is a cross-sectional view of a rotor sliding vane device having vanes and forced chambers along a plane passing through an inlet and an outlet. Variable capacity rotation between the rotor support part and the rotor coupling element, with a housing operation and support cover plate joined to the housing operating unit located between the rotor actuating part and the support part FIG. 2 is a cross-sectional view of a rotor sliding blade device having blades and a forced chamber, along a plane parallel to the surface of the rotor working surface and passing through an annular groove. Variable capacity rotation between the rotor support part and the rotor coupling element, with a housing operation and support cover plate joined to the housing operating unit located between the rotor actuating part and the support part FIG. 2 is a cross-sectional view of an annular deployment along an annular groove, which is a rotor sliding blade device having blades and a forced chamber. It is the schematic of the inclination angle changer of the support cover plate of a housing. FIG. 3 is an embodiment of a control valve in the form of a control slip valve selector having a slip valve stator window on a support cover plate of the housing and a selector switch on the slip valve stator window. FIG. Φ _merg with a normally closed bypass duct between the outlet hole and the transport hole and including an overall angle adjustment valve in the form of a back pressure valve _. It is the schematic of the whole angle adjustment means by the change of. _Φdeatch with a _closable bypass duct between the inlet hole and the transfer hole and including an overall angle adjustment valve _. It is the schematic of the whole angle adjustment means by the change of. 1 is an embodiment of an overall angle adjustment valve in the form of a piston-like slip valve selector in a bypass path. A rotor sliding vane device having a variable capacity forcing chamber between a working part of a rotor sliding along a support cover plate of the housing and a support part of the rotor, wherein the rotor and the housing are cut by 1/4 It is sectional drawing from the side of the operation part of a rotor. A rotor sliding vane device having a variable volume forced chamber between a working part of a rotor that slides along a support cover plate of the housing and a support part of the rotor, comprising an annular groove, a suction area, a forward conveying area, An annular development of the device along the pumping area and the rear transfer area is shown. A rotor sliding vane device having a variable capacity forcing chamber between a working part of a rotor sliding along a support cover plate of the housing and a support part of the rotor, wherein the rotor and the housing are cut by 1/4 It is sectional drawing from the side of the operation part of a rotor. A rotor sliding vane device having a variable capacity forcing chamber between an operating portion of a rotor that slides along a support cover plate of the housing and a support portion of the rotor, the rotor having a half cut of the housing FIG. 4 is a cross-sectional view from the side of the working part, where the working and supporting parts of the rotor are not shown. A rotor sliding vane device having a variable capacity forcing chamber between an operating portion of a rotor that slides along a support cover plate of the housing and a support portion of the rotor, the rotor having a half cut of the housing FIG. 3 is a cross-sectional view from the side of the working part, not showing the part of the support cover plate of the housing. A rotor sliding vane device having a variable capacity forcing chamber between the working part of the rotor sliding along the support cover plate of the housing and the support part of the rotor, in an annular deployment of the device along the annular groove Is a schematic diagram of means for adjusting the overall angle for the rear conveying hole in the form of a means for adjusting the overall magnitude of the change in the capacity of the conveying hole, a hydraulic duct to compensate, and a back-restricted bypass path having a back pressure valve; is there.

Claims (4)

A method for generating a non-fluid flow of working fluid,
Rotation of the rotor of the rotor sliding blade device;
Filling the inlet hole of the device with the working fluid at the inlet pressure;
Separation of the working fluid from the inlet hole by a vane of a transfer hole away from the outlet hole at an outlet pressure substantially not equal to the inlet pressure;
Conveying the working fluid in the conveying hole to the outlet hole;
Merging the transport hole to the outlet hole;
Movement of the working fluid to the outlet hole of the device while each conveying hole includes an intermediate vane and is separated from the inlet hole and outlet hole within a predetermined range of the rotation angle of the rotor;
Each transport hole includes at least one chamber of variable capacity formed in the rotor and connected to an intermediate vane of the transport hole, the capacity of the transport hole and the pressure of the working fluid therein Is changed in the course of transport due to a change in the volume of the chamber of variable capacity, and the pressure is substantially equal to the outlet pressure at the moment of confluence of the transport hole to the outlet hole.   The total width of the change in the capacity of the transport hole is increased when the movement amount of the rotor sliding blade device is increased, and the width is decreased when the movement amount is decreased. Method.   The method according to claim 1, wherein an increase in the difference between the inlet hole and the outlet hole increases the overall width of the change in the capacity of the transport hole and reduces it by decreasing the difference.   When the wave of the outlet pressure is detected and the moment of merging of the conveying hole with the outlet hole coincides with the rising surface of the wave of the outlet pressure, the conveyance is performed at the outlet pressure exceeding the inlet pressure. The method of claim 1, wherein the full width of the pore volume change is reduced and increased at the inlet pressure above the outlet pressure.

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