YAROSHENKO VIKTOR PROKOPOVYCH (UA)
WO2009104111A1 | 2009-08-27 | |||
WO2002097249A1 | 2002-12-05 |
DE888739C | 1953-09-03 | |||
NL6404846A | 1965-11-02 | |||
DE2258685A1 | 1974-06-20 |
Claims
[ 1 ] What is claimed is :
1. A rotary hydraulic machine comprising a body that comprises a main cylindrical cavity, inlet channels to feed a working fluid, and outlet channels to withdraw the working fluid; separating devices; and a rotor-piston which is installed within the main cylindrical cavity, comprises radial protrusions and radial recesses on the peripheral surface thereof, and forms, along with inner walls of the main cylindrical cavity, a plurality of closed segmental cavities, characterized in that each separating device is configured as a three-blade separating rotor installed within an unclosed separating chamber of the body which chamber is open to the main cylindrical cavity where the former crosses the latter; the side surfaces of the separating rotor blades are made concave with their radius of curvature being equal to that of the main cylindrical cavity; each separating rotor is installed with the possibility of descrete turn through 120° with stops so that, in its stop position, one of the side surfaces thereof forms a continuation of the inner substantially cylindrical surface of the main cylindrical cavity and the blade opposite to this side surface of the this rotor divides the separating chamber into a first section and a second section in the direction of separating rotor rotation; the inlet channels to feed the working fluid extend to the second sections of the separating chambers and outlet channels to withdraw the working fluid extend to the first sections of the separating chambers.
[2] 2. The rotary hydraulic machine as claimed in claim 1, characterized in that the number of the separating devices exceeds the number of the radial protrusions of the rotor-piston.
[3] 3. The rotary hydraulic machine as claimed in claim 2, characterized in that it comprises 8 separating devices and the rotor-piston comprises 6 radial protrusions. |
Description
ROTARY HYDRAULIC MACHINE
Technical Field
[1] The present invention relates to positive displacement hydraulic machines, and more particularly the present invention relates to hydraulic pumps, pneumatic pumps, hydraulic motors, and pneumatic motors. Among other applications, the present invention may be practiced in internal combustion engines, steam engines, gas generators, and other similar apparatuses. Background Art
[2] Hydraulic pumps and hydraulic motors are widely used in technology to pump or pressurize fluids, as well as to convert working fluid pressure into torque. In internal combustion engines, working fluid energy released in external combustion chambers is also converted into rotational energy.
[3] Well-known in the art are vane-type rotary hydraulic machines which comprise a body comprising an inner cylindrical cavity and side covers. The inner cylindrical cavity comprises a rotor-piston installed on a shaft. The rotor-piston comprises side surfaces which abut tightly against the side covers, an intake channel to feed working fluid, a discharge channel to withdraw working fluid, and separating elements in the form of separating vanes installed with possibility of radial reciprocal movement in rotor slots which abut against the inner surface of the body (see, e.g., U.S. Patent No.2,145,872, 1939; U.S. Patent No. 3,767,347, 1971; Hydraulics, Hydraulic Machines and Hydraulic Drive, Moscow, Vysshaya Shkola, 1965, p. 265; U.S. Patent No. 5 243 822, 1993). The vanes abut tightly against both side covers and inner surface of the body. The rotor-piston is installed within the body cavity so that, during the rotation thereof, the volume of each working cavity bounded by the rotor-piston, the pair of adjacent vanes and the inner surface of the body changes cyclically from the minimum volume Vmin to the maximum volume Vmax. The volume of a working cavity increases from the minimum volume Vmin to the maximum volume Vmax. (the intake stroke) when the working cavity communicates with the intake channel and decreases from the maximum volume down to the minimum volume when it communicates with the discharge channel (the exhaust stroke). The inner surface of the body is of such geometry that the intake stroke and the exhaust stroke are separated from each other, on the one hand, by at least one transfer zone in which the working volume communicates with neither the intake channel nor the discharge channel and has constant maximum value Vmax and, on the other hand, by at least one return zone in which the working volume communicates with neither the intake channel nor the discharge channel but has constant minimum value Vmin.
[4] Such hydraulic machine has a complex shape of the inner surface of the body which surface must have a variable curvature and a good surface finish in order to ensure a tight abutment of vanes and minimum losses due to vane friction. In addition, in such hydraulic machine, the vanes are subject to great side loads from the working fluid and, at the same time, reciprocate in rotor slots, this causing noticable losses and an increased wear of machine parts.
[5] The most similar to a hydraulic machine in accordance with this invention is a rotary hydraulic machine comprising a body that comprises an inner cylindrical cavity. The inner cylindrical cavity comprises a rotor-piston, which is concentrically mounted therein with the possibility of rotation. The rotor-piston comprises radial protrusions and radial recesses (United States patent No. 3,579,733, 1996). The inner cylindrical cavity communicates with an external source of working medium through an inlet channel and an outlet channel provided with controlled slide valves. The rotary hydraulic machine comprises also intake channels and discharge channels, separating devices in the form of vanes installed with possibility of radial reciprocal movement within the inner cylindrical cavity of the body between the inlet channel and the outlet channel and between the intake channel and the discharge channel. The separating devices form, along with the radial recesses of the rotor-piston and the inner surface of the substantially cylindrical cavity of the body, working cavities. In addition, the rotary hydraulic machine is provided with a separating vane control gear which feeds and retracts the separating vanes synchronously with rotor rotation so that their tight contact with the rotor surface is ensured without, however, a significant mechanical load on the contacting surfaces.
[6] In this hydraulic machine, the vanes are also subject to great side loads from the working fluid and, at the same time, reciprocate in rotor slots this causing noticable losses and an increased wear of machine part. Disclosure of Invention Technical Solution
[7] Accordingly, an object of the invention is to provide a hydraulic machine in which elements of separating devices will not reciprocate and, as a result, their wear and power losses will reduce.
[8] The object of the invention is achieved with a rotary hydraulic machine comprising a body that comprises a main cylindrical cavity, inlet channels to feed a working fluid, and outlet channels to withdraw the working fluid; separating devices; and a rotor- piston which is installed within the main cylindrical cavity, comprises radial protrusions and radial recesses on the peripheral surface thereof, and forms, along with inner walls of the main cylindrical cavity, a plurality of closed segmental cavities. The
rotary hydraulic machine is characterized in that each separating device is configured as a three-blade separating rotor installed within an unclosed separating chamber of the body which chamber is open to the main cylindrical cavity where the former crosses the latter; the side surfaces of the separating rotor blades are made concave with their radius of curvature being equal to that of the main cylindrical cavity; each separating rotor is installed with the possibility of discrete turn through 120° with stops so that, in its stop position, one of the side surfaces thereof forms a continuation of the inner substantially cylindrical surface of the main cylindrical cavity and the blade opposite to this side surface of the this rotor divides the separating chamber into a first section and a second section in the direction of separating rotor rotation; the inlet channels to feed the working fluid extend to the second sections of the separating chambers and outlet channels to withdraw the working fluid extend to the first sections of the separating chambers.
[9] Preferably, the number of the separating devices exceeds the number of the radial protrusions of the rotor-piston, most preferably, the machine comprises 8 separating devices and the rotor-piston comprises 6 radial protrusions. Description of Drawings
[10] The present invention will now be explained in more detail with reference to the accompanying drawings in which:
[11] Figs. 1 and 2 are the schematic views of the hydraulic machine in accordance with the present invention implemented as a pneumatic motor; and
[12] Figs. 3 and 4 are the schematic views of the hydraulic machine in accordance with the present invention implemented as a pump to pump a fluid. Industrial Applicability
[13] A rotary hydraulic machine in accordance with the present invention includes a body
1 that comprises a main cylindrical cavity. The main cylindrical cavity comprises a rotor-piston 2 (Figs. 1-4) mounted therein. The rotor-piston 2 comprises six radial protrusions 3-8 and six radial recesses 9-14 on the peripheral surface thereof. The six radial protrusions 3-8 and the six radial recesses 9-14 form, along with inner walls of the main cylindrical cavity, six closed segmental cavities 15-20. The body 1 is also provided with eight separating devices 21-28 configured as unclosed substantially cylindrical chambers open to the main cylindrical cavity of the body 1 in which chambers three-blade separating rotors 29-36 are installed. The rotors 29-36 are installed on conventional rotation supports and are kinematically connected to the rotor-piston 2 so that when the latter rotates continuously, the separating rotors 29-36 turn discretely through 120° with stops. The side surfaces of the blades of the separating rotors 29-36 are made concave with their radius of curvature being equal to
that of the main cylindrical cavity of the body 1. When the separating rotor is in its stop position, one of the side surfaces thereof always forms a continuation of the inner substantially cylindrical surface of the main cylindrical cavity of the body 1 and the blade opposite to this side surface of the this rotor divides the chamber of the corresponding separating device into a first section A and a second section B in the direction of separating rotor rotation.
[14] The separating chambers are provided with inlet channels 37 to feed a working fluid which extend to the second sections B of the separating chambers and outlet channels 38 to withdraw the working fluid which extend to the first sections A of the separating chambers.
[15] The rotor-piston 2 is installed at a shaft 39, which may serve as either a power takeoff shaft if the rotary hydraulic machine operates as a pneumatic motor or a hydraulic motor or a drive shaft if the rotary hydraulic machine operates as a pump to pump fluids.
[16] When the rotary hydraulic machine in accordance with the present invention operates as a pneumatic motor or a hydraulic motor (Figs. 1, 2), the inlet channels 37 are connected through a pressure regulator or a flow regulator (not shown) to a pressure working medium source and the outlet channels 38 are open to the environment or a waste working medium collector. The working medium may comprise a compressed gaseous medium (such as water steam, air, etc.) or a suitable liquid under pressure.
[17] When the rotary hydraulic machine in accordance with the present invention operates as a pneumatic pump or a hydraulic pump (Figs. 3, 4), the inlet channels 37 are open to a source of medium to be pumped, for example, to the environment and the outlet channels 38 are open to a receiver of medium to be pumped.
[18] In operation, the rotor-piston 2 rotates within the main cylindrical cavity of the body
1. The radial protrusions 3 - 8 of the rotor-piston 2 slide over the inner substantially cylindrical surface of the main cylindrical cavity of the body 1 and abut tightly against this surface so that to eliminate or minimize mass exchange between the segmental cavities 15-20.
[19] Each of the separating rotors 29-36 turns with stops which turns are synchronized with rotor-piston 2 rotation so that, at any time, either one of the tops of a separating rotor or one of the side surfaces thereof abuts tightly against the surface of the rotor- piston 2 with no gas flow through the conract area. This process may be described in more detail as follows. In the stop state, each of the separating rotors 29 - 36 is in such position that one of the side surfaces thereof forms a smooth continuation of the inner surface of the main cylindrical cavity of the body 1, and one of the radial protrusions 3-8 of the rotor-piston 2 slides over this surface. The separating rotors 30, 31, 34 and 35 in Figs. 1, 3 and the separating rotors 29, 30, 33 and 34 in Fig. 2, 4 are in the stop
state.
[20] The separating rotor goes into a static state at that point of time when the leading edge of a protrusion of the rotor-piston 2 reaches the opening between the separating chamber and the main cylindrical cavity of the body 1. This protrusion of the rotor- piston slides then over the side surface of a immovable separating rotor whose opposite protrusion divides the separating chamber into the first cavity A and the second cavity B in the direction of separating rotor rotation isolated from the segmental cavities 15-20.
[21] When the protrusion of the rotor-piston 2 completely leaves the side surface of a separating rotor, the separating rotor starts turning. During this turn, the top of the separating rotor slides with no gap over the surface of a radial recess of the rotor-piston 2. The separating rotor turns through 120° and stops when the leading edge of the next following radial protrusion of the rotor-piston 2 reaches the opening to the separating chamber; at that point of time, the separating rotor of this separating chamber goes into a static position and, thereafter, this radial protrusion slides over the side surface of this separating rotor.
[22] During the turn of the separating rotor, it forms, along with the walls of the separating chamber:
[23] an increasing chamber C;
[24] an isolated chamber E; and
[25] a decreasing chamber K.
[26] At the same time, a blade of this separating rotor slides over the surface of a radial recess of the rotor-piston 2 and divides the corresponding segmental cavity into an increasing chamber P and a decreasing chamber T.
[27] The separating rotor 35 of the chamber 27 in Fig. 1 is in a static state, and the radial protrusion 8 of the rotor-piston 2 slides over a side surface thereof. The chamber 27 is divided into two isolated cavities A and B. The cavity A communicates through the outlet channel 38 with the environment and, as a result, the working fluid, for example, air, leaves the chamber 27 and the air pressure therein become close to the atmospheric pressure. During this period of time, the cavity B is connected through a pressure regulator to a high pressure air source, is filled with this air, and pressure therein rises.
[28] The separating rotor 36 of the chamber 28 in Fig. 1 is turning; one of the protrusions thereof slides over the surface of the radial recess 14 of the rotor-piston 2. The segmental cavity 20 is divided into an increasing cavity P and a decreasing cavity T. The cavity E communicates through the outlet channel 38 with the environment and, as a result, the working fluid continues to leave it. During this period of time, the cavity K is connected through a pressure regulator to a high pressure air source, is filled with this air, and pressure therein reaches the maximum level set by the pressure regulator.
This cavity K communicates with the increasing cavity P whose air pressure is also equal or close to the maximum pressure. The cavities T and C are also filled with air at the maximum pressure and, as a result, the air pressure resultant within the cavities T and P is directed at the rotor-piston rotation axis and produces no torque.
[29] The separating rotor 29 of the chamber 21 in Fig. 1 is turning; one of the protrusions thereof slides over the surface of the radial recess 9 of the rotor-piston 2. The segmental cavity 15 is divided into an increasing cavity P and a decreasing cavity T. The joint cavities C and T communicate through the outlet channel 38 with the environment and, as a result, the working fluid is leaving them. During this period of time, the cavities K and P are connected through a pressure regulator to a high-pressure air source, are filled with this air, and pressure therein is close to the maximum level set by the pressure regulator. Due to pressure difference between the cavities P and T, the resultant force R is produced directed away from the rotor-piston 2 rotation axis and, as a result, torque is produced which sets the rotor-piston 2 in rotation.
[30] The separating rotor 30 of the chamber 22 in Fig. 1 is in a static state which is characterized by the processes described above for the separating rotor 35 of the chamber 27.
[31] In the pairs of the opposite separating chambers, substantially identical processes occur and, therefore, radial loads on the rotor-piston are balanced and tangential loads are summed up into torque which is transmitted to the power take-offshaft 39. In addition, working medium pressure on the separating rotor blades produces no torque and, as a result, the control of the separating rotors does not require noticeable power inputs.
[32] Fig. 2 shows the positions of the machine elements when the rotor-piston has turned forward through 22°. Here, torque is produced thanks to the positions of the separating rotors 35 and 31 whilst the other separating rotors are in their static state.
[33] When the rotary hydraulic machine in accordance with the present invention operates as a pump (Figs. 3 and 4), the inlet channels 37 are connected to a source of medium to be pumped (not shown) and the outlet channels 38 are connected to a receiver of medium to be pumped (not shown). A medium to be pumped may comprise any fluid which is compatible with the materials of machine parts, such as gas, liquid, suspension, among others.
[34] In operation, the rotor-piston 2 is driven by an external power supply and rotates within the main cylindrical cavity of the body 1. The radial protrusions 3 - 8 of the rotor-piston 2 slide over the inner substantially cylindrical surface of the main cylindrical cavity of the body 1 and abut tightly against this surface so that to eliminate or minimize mass exchange between the segmental cavities 15-20.
[35] Each of the separating rotors 29-36 turn with stops which turns are synchronized
with rotor-piston 2 rotation as described above.
[36] During the rotation of the rotor-piston 2, vacuum is created within the decreasing cavities P, thereby the medium pumped is sucked through inlet channels 37 through the cavities K of the separating chambers and fills the corresponding segmental cavities of the rotor-piston 2. The medium further pumped is carried by these segmental cavities to the separating cavities next following in the direction of rotation and, due to reduction in the volume of the cavities T, is pressed out to the receiver of the medium pumped through the cavities C of the separating cavities and the outlet channels 38.
[37] In this example as well, in the pairs of the opposite separating chambers, substantially identical processes occur and, therefore, radial loads on the rotor-piston are balanced.
[38] Thus, in the rotary hydraulic machine in accordance with the present invention, power losses due to friction of the elements of separating devices are minimized because the separating rotors rotate freely on conventional rotation supports and radial loads are carried by these supports. The rotary hydraulic machine in accordance with the present invention comprises neither valves to control working fluid flows nor radial vanes which reciprocate; hydrodynamic resistance to working fluid flows may also be minimized by making channels for them both wide and short.
[39] The preceding detailed description is not intended to be limited to the specific forms set forth herein, but on the contrary, it is intended to cover such alternatives, modifications, and equivalents devised by those skilled in the art, as can be reasonably included within the spirit and scope of the appended claims.