Patent Description:
Spherical pump is an emerging positive displacement mechanism, which has no intake/exhaust valves and few moving parts. The moving parts are in surface contact (namely, forming a surface sealing structure), which can achieve the high-pressure condition and structural miniaturization. Currently, the spherical pump has been extensively applied in practice. Nevertheless, there is a fixed angle between the piston axis and the main shaft, and the pressure in the two working chambers experiences a back-and-forth change, such that there is a pressure difference between the two chambers. As a result, the piston and the rotating disc will deflect toward the lower pressure side to squeeze the spherical surface of the cylinder body to render the gap between the rotating disc and the spherical surface of the cylinder body smaller, which will cause damages to the oil film or water film, and an increase in the friction force, leading to increased energy consumption, and serious abrasion of the rotor and the slipper.

Chinese patent (<CIT>) discloses a spherical pump. The spherical pump includes a cylinder cover <NUM>, a cylinder body <NUM>, a piston <NUM>, a turntable <NUM>, a main shaft <NUM> and a main shaft bracket <NUM>. The cylinder cover <NUM> is connected with an upper end of the cylinder body <NUM> to form a spherical inner cavity. A sliding groove <NUM> is formed in an upper end face of the main shaft <NUM>. A slipper <NUM> at the end of a turntable shaft is inserted into the sliding groove <NUM> in an upper end of the main shaft <NUM>. The piston <NUM> is hinged to the turntable <NUM> and movably connected with the main shaft <NUM>. When the main shaft <NUM> rotates, the slipper <NUM> slides in the sliding groove <NUM> in a reciprocating mode, the piston <NUM> and the rotary disc <NUM> swing relatively, and two working chambers <NUM> with the volumes changing alternately are formed in the spherical inner cavity.

Chinese patent application (<CIT>) discloses a spherical compressor. A cylinder body <NUM> and a cylinder cover <NUM> are combined to form a spherical inner cavity. A slide groove swing mechanism is arranged between a piston shaft <NUM> and a piston shaft hole <NUM> or between a rotating plate shaft <NUM> and a rotating plate shaft hole <NUM>. The rotating plate shaft <NUM> is driven to rotate to enable a piston <NUM> to swing relative to an axis of the piston shaft hole <NUM> along a slide groove of the slide groove swing mechanism between the piston shaft <NUM> and the piston shaft hole <NUM> or swing relative to an axis of the rotating plate shaft hole <NUM> along the slide groove of the slide groove swing mechanism between the rotating plate shaft <NUM> and the rotating plate shaft hole <NUM>. Consequently, an operation chamber V<NUM> and an operation chamber V<NUM> in alternate volume variation are formed in the spherical inner cavity.

Chinese patent application (<CIT>) discloses a spherical pump which includes a cylinder cover <NUM>, a cylinder body <NUM>, a piston <NUM>, a rotary table <NUM>, a spindle <NUM> and a spindle bracket <NUM>. The cylinder cover <NUM> is connected with an upper end of the cylinder body <NUM> to form a spherical cavity. A sliding chute <NUM> is formed in an upper end face of the spindle <NUM>. A slipper <NUM> at an end of the rotary table shaft is inserted in the sliding chute <NUM>. The piston <NUM> is hinged to the rotary table <NUM> and then is movably connected with an upper end of the spindle <NUM> to constitute a rotor. When the spindle <NUM> rotates, the slipper <NUM> reciprocates in the sliding chute <NUM>, the piston <NUM> and the rotary table <NUM> swing relatively, and two working chambers <NUM> with the volumes changing alternately are formed in the spherical cavity. Chinese patent (<CIT>) discloses a bidirectional rotating spherical pump cooling mechanism. An inlet and outlet hole <NUM>, a cylinder cover flow dividing channel <NUM>, a cylinder body flow dividing channel <NUM> and a cylinder body flow guiding channel <NUM> are sequentially communicated to form a flow dividing part of a cooling channel. A main shaft support flow guide groove <NUM>, a cylinder body lower backflow channel <NUM>, a cylinder body upper backflow channel <NUM>, a cylinder cover backflow channel <NUM> and the inlet and outlet hole <NUM> are sequentially communicated to form a backflow part of the cooling channel. A switching valve is arranged on the cylinder body <NUM> and controls connection of the cylinder body flow guiding channel <NUM> and connection between the cylinder body lower backflow channel <NUM> and the cylinder body upper backflow channel <NUM>.

PCT patent application (<CIT>) discloses a positive displacement device that converts energy, namely positive displacement compressors that rotate in a single rotational direction to displace working fluid contained in operating chambers. US patent application (<CIT>) discloses a journal bearing for a shaft includes a pair of axially displaced seals between the shaft and its housing, one of the seals lying in a plane inclined to the normal to the shaft axis. A fluid pressure introduced between the seals applies a couple to the shaft which opposes an externally applied couple tending to move the axis of the shaft with respect to the axis of a bore in the housing.

US patent (<CIT>) discloses shroud arrangements to be used in rotary engines using a plurality of rotors within the shroud arrangement. At least one of the rotors is not fixed to the shroud.

An object of the present invention is to provide a spherical pump having a hydrostatic pressure support, whose rotor slipper is provided with the hydrostatic pressure support to balance the unbalanced force during the operation by means of the hydraulic pressure generated by the spherical pump, facilitating reducing the energy consumption and prolonging the service life of the spherical pump.

Technical solutions of the present invention are described as follows.

This invention provides a spherical pump, comprising:.

Compared to the prior art, the present invention has the following beneficial effects.

The embodiments of the disclosure will be illustrated in detail below with reference to the accompanying drawings.

In the drawings: <NUM>, cylinder cover; <NUM>, piston; <NUM>, central pin; <NUM>, rotating disc; <NUM>, cylinder body; <NUM>, main shaft; <NUM>, main shaft bracket; <NUM>, bearing; <NUM>, sealing ring; <NUM>, slipper liner; <NUM>, cylinder liner; <NUM>, suction port; <NUM>, throttling step; <NUM>, discharge port; <NUM>, first diversion channel; <NUM>, piston shaft hole; <NUM>, waist-shaped inlet hole; <NUM>, waist-shaped outlet hole; <NUM>, first returning channel; <NUM>, chip groove; <NUM>, piston main body; <NUM>, first PEEK layer; <NUM>, spherical top surface; <NUM>, piston shaft; <NUM>, first pin seat; <NUM>, side surface; <NUM>, first pin hole; <NUM>, opening; <NUM>, rotating disc main body; <NUM>, second PEEK layer; <NUM>, slipper; <NUM>, first liquid flow channel; <NUM>, first inlet; <NUM>, first outlet; <NUM>, second liquid flow channel; <NUM>, second inlet; <NUM>, second outlet; <NUM>, first pressure-bearing groove; <NUM>, second pressure-bearing groove; <NUM>, first multi-stage rectangular groove; <NUM>, first rectangular primary pressure-bearing groove; <NUM>, first rectangular auxiliary pressure-bearing groove; <NUM>, second multi-stage rectangular groove; <NUM>, second rectangular primary pressure-bearing groove; <NUM>, second rectangular auxiliary pressure-bearing groove; <NUM>, first multi-stage circular groove; <NUM>, first circular primary pressure-bearing groove; <NUM>, first circular auxiliary pressure-bearing groove; <NUM>, second multi-stage circular groove; <NUM>, second circular primary pressure-bearing groove; <NUM>, second circular auxiliary pressure-bearing groove; <NUM>, rotating disc shaft; <NUM>, second pin hole; <NUM>, second pin seat; <NUM>, second diversion channel; <NUM>, second returning channel; <NUM>, through hole; <NUM>, sliding groove; <NUM>, overflow hole; <NUM>, returning groove; and <NUM>, working chamber.

To render the technical solutions, objects and advantages of the present disclosure clearer, the embodiments of the disclosure will be described in detail below with reference to the accompanying drawings.

As shown in <FIG>, a spherical pump provided herein includes a cylinder cover <NUM>, a piston <NUM>, a rotating disc <NUM>, a cylinder body <NUM>, a main shaft <NUM>, and a main shaft bracket <NUM>. Both the cylinder body <NUM> and the cylinder cover <NUM> have a hemi-spherical inner cavity. The cylinder body <NUM>, the cylinder cover <NUM>, and the main shaft bracket <NUM> are sequentially connected by screws to form a spherical pump casing having a spherical inner cavity, that is, a spherical pump stator. The piston <NUM>, the rotating disc <NUM> and the main shaft <NUM> are connected in sequence to form a spherical pump rotor. The main shaft bracket <NUM> is configured to provide support for the rotation of the main shaft <NUM>, and is fixedly connected to a lower end of the cylinder body <NUM> by screws. The piston <NUM> and the rotating disc <NUM> are hinged via a central pin <NUM>, and the piston shaft <NUM> is inserted into the piston shaft hole <NUM> inside the cylinder cover <NUM>. A slipper <NUM> at a lower end of the rotating disc shaft is inserted into a sliding groove <NUM> at an upper end of the main shaft <NUM>.

As shown in <FIG>, an upper end of the cylinder cover <NUM> is provided with a suction port <NUM> and a discharge port <NUM>, and an inner spherical surface of the cylinder cover <NUM> is provided with a waist-shaped inlet hole <NUM>, a waist-shaped inlet hole <NUM> and a piston shaft hole <NUM>. An axis of the piston shaft hole <NUM> passes through the sphere center of the inner spherical surface of the cylinder cover <NUM>. The waist-shaped inlet hole <NUM> and the waist-shaped inlet hole <NUM> are arranged in an annular area perpendicular to the axis of the piston shaft hole <NUM>. The waist-shaped inlet hole <NUM> is in communication with the suction port <NUM> at the upper end of the cylinder cover <NUM>, and the waist-shaped outlet hole <NUM> is in communication with the discharge port <NUM> at the upper end of the cylinder cover <NUM>. The suction/discharge of liquid is realized by controlling the rotation of the piston <NUM>. When it is required to suck or discharge the liquid, the working chamber is connected to the waist-shaped inlet hole <NUM> or the waist-shaped outlet hole <NUM>. To prevent chips generated by the rotation of the piston shaft <NUM> in the piston shaft hole <NUM> from entering a gap between the outer spherical surface of the piston <NUM> and the inner spherical surface of the cylinder cover <NUM>, a chip groove <NUM> is provided on the inner spherical surface of the cylinder cover <NUM>. One end of the chip groove108 is communicated with the waist-shaped inlet hole <NUM>, the other end of the chip groove <NUM> extends near to the opening of the piston shaft hole <NUM> along the inner spherical surface of the cylinder cover <NUM> in the direction of the piston shaft hole <NUM>. The cross section of the chip groove <NUM> is U-shaped, and the U-shaped opening is located on the inner spherical surface of the cylinder cover <NUM>. The cross-sectional sizes of the chip groove <NUM> (i.e., depth and width) are designed based on the principle that the spherical pump is non-leakage. The chip groove <NUM> can be communicated with the piston shaft hole <NUM> or not communicated with the piston shaft hole <NUM>. In this manner, chips discharged from the piston shaft hole <NUM> gather in the chip groove <NUM>, enter the working chamber <NUM> with the liquid, and flow with the liquid to be out of the cylinder.

As shown in <FIG>, the lower end of the cylinder body <NUM> is provided with a through hole <NUM> communicated with the outside, and the through hole <NUM> is configured to allow a rotating disc shaft to pass through. The size of the through hole <NUM> is designed to ensure that the rotating disc shaft does not interact with the cylinder body <NUM> during the rotation of the rotating disc <NUM>. A part where the main shaft <NUM> and the lower end of the cylinder body <NUM> are matched is provided with a cylinder liner <NUM>. A cylinder liner hole is provided at the lower end of the cylinder body <NUM>, and the cylinder liner <NUM> is placed in the cylinder liner hole configuring for a rotating support for the upper end of the main shaft <NUM> (equivalent to a sliding bearing) during rotation of the main shaft <NUM>. The axes of the cylinder liner hole, the cylinder liner <NUM> and the main shaft <NUM> are coincided, and both pass through the sphere center of the inner spherical surface of the cylinder. The inner diameter of the cylinder liner <NUM> is matched with the upper shaft neck of the main shaft <NUM>, and the outer diameter of the cylinder liner <NUM> is matched with the inner diameter of the cylinder liner hole. The cylinder liner <NUM> is cylindrical, and made of poly(ether-ether-ketone) (PEEK). The outer cylindrical surface and the inner cylindrical surface of the cylinder liner <NUM> are respectively provided with a cooling groove penetrating along the axial direction of the cylinder liner <NUM>, which are configured to cool and lubricate the main shaft <NUM> and the cylinder liner <NUM> through the cooling liquid.

As shown in <FIG>, the piston <NUM> has a spherical top surface <NUM>, two side surfaces <NUM> at an angle α (<NUM>-<NUM>°), and a first pin seat is provided <NUM> at the lower portion of the two side surfaces <NUM>. A piston shaft <NUM> protrudes from a middle of the spherical top surface <NUM> of the piston <NUM>. The axis of the piston shaft <NUM> passes through the sphere center of the spherical top surface <NUM> of the piston <NUM>. The piston shaft <NUM> is inserted into the piston shaft hole <NUM> on the inner spherical surface of the cylinder cover <NUM>. The spherical top surface <NUM> of the piston <NUM> and the spherical inner cavity of the cylinder cover <NUM> have the same sphere center, and the spherical top surface <NUM> of the piston <NUM> is in a sealing movable fit with the spherical inner cavity of the cylinder cover <NUM>. The first pin seat <NUM> is semi-cylindrical, and provided with a first pin hole <NUM> penetrating along the central axis of the piston pin seat <NUM>. An opening <NUM> is provided on the first pin seat <NUM> at the lower portion of the piston <NUM> to form a semi-cylindrical groove. The opening <NUM> of the piston <NUM> is located in the middle of the first pin seat 204and is vertical to the axis of the first pin hole <NUM> of the piston pin seat <NUM>, and the width of the opening <NUM> of the piston <NUM> is matched with the width of the convex semi-cylinder of the second pin seat <NUM>. In actual production, the piston <NUM> is made of a stainless-steel metal base, that is, the piston main body <NUM> is covered with a PEEK layer (namely, first PEEK layer <NUM>) by injection molding to ensure that the spherical top surface <NUM> of the piston, the outer cylindrical surface and the two side surfaces <NUM> of the first pin seat <NUM>, two side surfaces and the circular arc bottom surface of the semi-cylindrical groove of the first pin seat <NUM>, and the cylindrical surface of the piston shaft <NUM> are all coated with the PEEK layer, so that the moving part forms a friction pair between the stainless steel and the PEEK layer. The PEEK has abrasion resistance, high strength, corrosion resistance and self-lubricating properties, which is good wear-resistant material, and has good friction matching performance with stainless steel.

As shown in <FIG>, the rotating disc <NUM> is provided with a pin seat of the rotating disc <NUM> corresponding to the piston pin seat <NUM>. A rotating disc shaft <NUM> protrudes from the center of the lower end of the rotating disc <NUM>, and the rotating disc shaft <NUM> passes through the center of the spherical surface of the rotating disc. The end of the rotating disc shaft <NUM> is provided with a slipper <NUM>. The outer peripheral surface between the upper and lower end surfaces of the rotating disc <NUM> is a spherical surface of the rotating disc, which has the same spherical center with the spherical inner cavity and is close to the spherical inner cavity. The spherical surface of the rotating disc is fitted with the spherical inner cavity in a sealed movable manner. Two ends of the second pin seat <NUM> both are a semi-cylindrical groove, the middle portion of the second pin seat <NUM> is a convex semi-cylinder, and a through second pin hole <NUM> is provided at the center of the semi-cylinder. The central pin <NUM> is inserted into the second pin hole <NUM> and the first pin hole <NUM> to form a cylindrical hinge. Individual matching surfaces of the cylindrical hinge are in a sealing movable fit. Two ends of the cylindrical hinge are respectively in a sealing movable fit with the spherical inner cavity. The piston <NUM> and the rotating disc <NUM> form a sealing movable connection through the cylindrical hinge. The two ends of the central pin <NUM> are respectively provided with an arc insert made of PEEK. The arc shape of the arc insert is matched with the shape of the spherical inner cavity. In the actual production, the rotating disc <NUM> is made of a stainless-steel metal base, that is, the rotating disc base <NUM> is coated with a PEEK layer (that is, second PEEK layer <NUM>) by injection molding to ensure that the spherical surface of the rotating disc, slipper <NUM>, and two parallel sides adhered to the sliding groove <NUM> are all coated with the PEEK layer, so that the moving part forms a friction pair between the stainless steel and the PEEK layer. Two ends of the central pin <NUM> both are an arc surface. The cylindrical surface of the matching part between the central pin <NUM> and the pin hole formed by the first pin seat <NUM> and the second pin seat <NUM> is made of PEEK. To ensure the strength of the central pin <NUM>, the central pin is coated with a layer of PEEK material on the steel substrate.

As shown in <FIG>, the main shaft bracket <NUM> is fixedly connected to the lower end of the cylinder body <NUM> by screws, and the main shaft <NUM> is connected to the lower end of the cylinder body <NUM> through the main shaft bracket <NUM>. The upper end surface of the main shaft <NUM> is provided with a rectangular sliding groove <NUM>, and the cross-sectional size of the sliding groove <NUM> is matched with the thickness between the two parallel sides of the slipper <NUM> on the rotating disc <NUM>. The rotating disc shaft extends from the lower end of the cylinder body <NUM>, and the slipper <NUM> is inserted into the sliding groove <NUM> at the upper end of the main shaft <NUM>. The two parallel sides of the slipper <NUM> are attached to the two sides of the sliding groove <NUM> to respectively form a sliding fit. A bearing <NUM> and a sealing ring <NUM> are provided at the matching part between the lower end of the main shaft <NUM> and the main shaft bracket <NUM>. The returning groove <NUM> is provided on the hole wall of the shaft hole of returning groove <NUM>, which is communicated with the second returning channel <NUM> on the lower end surface of the cylinder body <NUM>, and the bottom surface of the sliding groove <NUM> is provided with the overflow hole <NUM>. The overflow hole <NUM> is configured to introduce the liquid at the upper end of the main shaft <NUM> into the gap (above the seal ring <NUM>) of the matching part between the lower end shaft neck of the main shaft <NUM> and the main shaft bracket <NUM>, and then flow back from the returning groove <NUM> to the second returning channel <NUM>. The main shaft bracket <NUM> provides a support for the rotation of the main shaft, and the lower end of the main shaft <NUM> is connected with the power mechanism to provide power for the operation of the spherical pump.

The cylinder cover <NUM> is provided with a first diversion channel <NUM> and a first returning channel <NUM>. The cylinder body <NUM> is provided with a second diversion channel <NUM> and a second returning channel <NUM>. The upper ends of the first diversion channel <NUM> and the first returning channel <NUM> are respectively communicated with the suction port <NUM>. The lower ends of the first diversion channel <NUM> and the first returning channel <NUM> are both arranged on the flange surface of the lower end of the cylinder cover <NUM>. The upper ends of the second diversion channel <NUM> and the second returning channel <NUM> are both arranged on the flange surface of the upper end of the cylinder body <NUM>. The lower end of the first diversion channel <NUM> is connected to the upper end of the second diversion channel <NUM>, and the upper end of the second returning channel <NUM> is connected to the first returning channel <NUM>. The lower end of the second returning channel <NUM> is connected to the returning groove <NUM>. A throttling step <NUM> is provided in the suction port <NUM>. The liquid in the suction port <NUM> is throttled by the throttle surface and mainly enters the working chamber <NUM>, and the rest liquid enters the cooling channel to cool the system. The first diversion channel <NUM>, the second diversion channel <NUM>, the liquid collection tank, the returning groove <NUM>, the second returning channel <NUM>, and the first returning channel <NUM> are connected in sequence to form a cooling channel of the spherical pump. The inlet of the cooling channel is communicated with the suction port <NUM>. The cooling liquid flowing from the suction port <NUM> sequentially passes through the first diversion channel <NUM> and the second diversion channel <NUM> to enter the cavity formed by the lower end of the cylinder body, the upper end of the main shaft <NUM> and the upper end of the main shaft bracket <NUM> to form a liquid collecting pool, then passes through the returning groove <NUM>, the second returning channel <NUM> and the first returning channel <NUM> to flow back into the suction port <NUM>, and then is sucked into the working chamber <NUM> to form a cooling circulation system of the spherical pump.

The axes of the piston shaft hole <NUM> and the rotating disc shaft <NUM> pass through the center of the spherical inner cavity, and both have an angle α with the axis of the main shaft <NUM>. The two parallel sides of the slipper <NUM> are symmetrically arranged on two sides of the axis of the rotating disc and parallel to the axis of the cylindrical hinge. When the main shaft <NUM> rotates to drive the rotating disc <NUM> and the piston <NUM>, the slipper <NUM> slides back and forth in the sliding groove <NUM>, and the piston <NUM> and the rotating disc <NUM> swing in relation to each other. Two working chambers <NUM> with alternating volumes are formed between the upper end surface of the rotating disc <NUM>, the two sides of the piston <NUM> and the spherical inner cavity. When one working chamber <NUM> sucks liquid, the other working chamber <NUM> compresses to drain. When the main shaft <NUM> goes through a full rotation, the piston <NUM> rotates one circle around the axis of the piston shaft hole <NUM>, and swings once about the axis of the central pin <NUM> relative to the rotating disc <NUM>, and at the same time, the slipper <NUM> of the rotating disc <NUM> swings once in the sliding groove <NUM> of the main shaft <NUM> with the swing amplitude of 2α, and the two working chambers <NUM> each undergo a complete liquid suction or compression discharge process.

As shown in <FIG>, <FIG>, and <FIG>, a static pressure support is provided between the two parallel sides of the slipper <NUM> of the rotating disc <NUM> and the sliding groove <NUM>, which includes a first liquid flow channel <NUM> and a second liquid flow channel <NUM> that are both arranged on the rotating disc, and a first pressure-bearing groove <NUM> and a second pressure-bearing groove <NUM> respectively arranged on the two parallel sides of the slipper <NUM>.

The rotating disc <NUM> is provided with the first liquid flow channel <NUM> and the second liquid flow channel <NUM>. The first liquid flow channel <NUM> includes a first inlet <NUM>, a first channel and a first liquid flow channel outlet <NUM>. The first inlet <NUM> is arranged on the upper end surface of the rotating disc <NUM> and is communicated with a working chamber <NUM>. The first liquid flow channel outlet <NUM> is arranged on one of the two parallel sides of the slipper <NUM>. The first inlet <NUM> and the first liquid flow channel outlet <NUM> are respectively located on two sides of a plane parallel to the two parallel sides of the slipper <NUM> where the axis of the rotating disc is located (the plane is parallel to the two parallel sides of the slipper <NUM> and passes through the center of the spherical surface of the rotating disc). The first channel and the second channel are independent in the rotary channel <NUM>. The slipper <NUM> is arranged in the sliding groove <NUM>. Two parallel sides of the slipper <NUM> are respectively in a sliding fit with the two parallel sides of the sliding groove <NUM>. A hydrostatic pressure support is provided between each of the two parallel sides of the slipper <NUM> and the sliding groove <NUM> of the spherical pump to facilitate processing and reduce the friction between the slipper <NUM> and the sliding groove <NUM>. Preferably, a slipper liner <NUM> is provided between each of the two parallel sides of the slipper <NUM> and the sliding groove <NUM>, which is plate-shaped and made of PEEK. Two slipper liner <NUM> are respectively arranged at the two parallel sides of the slipper <NUM>, one side of each slipper liner <NUM> is attached to a side of the sliding groove <NUM>, and the other side of each slipper liner <NUM> is attached to one of the two parallel sides of the slipper <NUM>. The slipper liner <NUM> can be integrated with the slide groove <NUM> after being fixed. During processing, two sides of each slipper liner <NUM> are respectively attached to the two sides of the slipper <NUM>, the two parallel sides of the slipper <NUM> are respectively fit with slipper liners <NUM> on both sides, and the slipper <NUM> is configured to slide back and forth along surfaces of the slipper liner <NUM>. The first pressure-bearing groove <NUM> and the second pressure-bearing groove <NUM> are respectively provided on the two parallel sides of the slipper <NUM>. The first outlet <NUM> is communicated with the first pressure-bearing groove <NUM>, and the second outlet <NUM> is communicated with the second pressure-bearing groove <NUM>. Through minimizing the flow area of the first outlet <NUM> and the second outlet <NUM>, to control the liquid flow rate of the hydrostatic pressure support, and avoid the obvious descending of volumetric efficiency. The cross-sectional size of the first pressure-bearing groove <NUM> is much larger than that of the first outlet <NUM>, and the cross-sectional size of the second pressure-bearing groove <NUM> is much larger than that of the second outlet <NUM>. The first pressure-bearing groove <NUM> and the second pressure-bearing groove <NUM> are respectively recessed on the two parallel sides of the slipper <NUM>, generally having a depth of <NUM>. The diameters of the first outlet <NUM> and the second outlet <NUM> are both <NUM>-<NUM>. To increase the liquid supporting force of the hydraulic support, The cross-sectional areas of the first pressure-bearing groove <NUM> and the second pressure-bearing groove <NUM> are designed as large as possible, that is, the cross-sectional size of the first pressure-bearing groove <NUM> is over <NUM> times than that of the first liquid flow channel outlet <NUM>, and the cross-sectional size of the second pressure-bearing groove <NUM> is over <NUM> times than that of the second outlet <NUM>. During the operation of the spherical pump, when the working chamber <NUM> communicated with the first liquid flow channel <NUM> is at high pressure, the rotor as a whole will unidirectionally squeeze the side of the slipper <NUM> where the first pressure-bearing groove <NUM> is provided (namely, the side where the working chamber <NUM> at low pressure is located) to reduce the gap between the side of the slipper <NUM> provided with the first pressure-bearing groove <NUM> and the slipper liner <NUM> arranged in the sliding groove <NUM>, and at the same time, the gap between the side of the spherical surface of the rotating disc provided with the first pressure-bearing groove <NUM> and the spherical inner cavity is correspondingly reduced, the friction force between the side of the slipper provided with the first pressure-bearing groove <NUM> and the slipper liner <NUM> is also reduced accordingly, and the friction between the spherical surface of the rotating disc and the spherical inner cavity is increased. However, the high-pressure liquid in the first liquid flow channel <NUM> enters the first pressure-bearing groove <NUM> at this time to generate a large hydraulic pressure, which acts as a static pressure support between the side of the slipper <NUM> and the slipper liner <NUM>, thereby balancing the unidirectional squeezing on the rotor caused by the high pressure of the working chamber connected to the first liquid flow channel <NUM>, increasing the gap between the side of the slipper <NUM> provided with the first pressure-bearing groove <NUM> and the slipper liner <NUM> to a preset value, and normalizing the gap between the spherical surface of the rotating disc and the spherical inner cavity, which lowers the friction between the mating surfaces when the spherical pump is running, reduces the power consumption of the spherical pump, and extends the normal service life of the spherical pump.

In the same way, the working chamber <NUM> communicated with the second liquid flow channel <NUM> is at high pressure, the rotor as a whole will unidirectionally squeeze the side of the slipper <NUM> where the second pressure-bearing groove <NUM> is provided (namely, the side where the working chamber <NUM> at low pressure is located) to reduce the gap between the side of the slipper <NUM> provided with the second pressure-bearing groove <NUM> and the slipper liner <NUM> arranged in the sliding groove <NUM>, and at the same time, the gap between the side of the spherical surface of the rotating disc provided with the second pressure-bearing groove <NUM> and the spherical inner cavity is correspondingly reduced, the friction force between the side of the slipper provided with the second pressure-bearing groove <NUM> and the slipper liner <NUM> is also reduced accordingly, and the friction between the spherical surface of the rotating disc and the spherical inner cavity is increased. However, the high-pressure liquid in the second liquid flow channel <NUM> enters the second pressure-bearing groove <NUM> at this time to generate a large hydraulic pressure, which acts as a static pressure support between the side of the slipper <NUM> and the slipper liner <NUM>, thereby balancing the unidirectional squeezing on the rotor caused by the high pressure of the working chamber connected to the second liquid flow channel <NUM>, increasing the gap between the side of the slipper <NUM> provided with the second pressure-bearing groove <NUM> and the slipper liner <NUM> to a preset value, and normalizing the gap between the spherical surface of the rotating disc and the spherical inner cavity.

The spherical pump runs cyclically, and the two working chambers <NUM> alternately generate high pressure. The first liquid flow channel <NUM> and the second liquid flow channel <NUM> are alternately communicated with the high-pressure working chamber <NUM>, constantly balancing the unbalanced force during the running of the rotor, and adjusting the gaps between the working surfaces, which lowers the friction between the mating surfaces when the spherical pump is running, reduces the power consumption of the spherical pump, and extends the normal service life of the spherical pump.

In this application, the pressure-bearing groove can be rectangular, circular or other shapes, and is arranged at the sphere center of each of the two parallel sides of the slipper <NUM>. The pressure-bearing groove can also be designed as a multi-stage pressure-bearing groove, that is, the multi-stage liquid pressure-bearing groove, which can also be a multi-stage circular groove or a multi-stage rectangular groove. The multi-stage pressure-bearing groove includes a first multi-stage pressure-bearing groove arranged at the center of one of the two parallel sides of the slipper <NUM>, and a second multi-stage pressure-bearing groove arranged at the center of the other of the two parallel sides of the slipper <NUM>. The first liquid flow channel outlet <NUM> is connected to the first multi-stage pressure-bearing groove, and the second outlet <NUM> is connected to the second multi-stage pressure-bearing groove. The cross-sectional size of the first multi-stage pressure-bearing groove is larger than that of the first liquid flow channel outlet <NUM>, and the cross-sectional size of the second multi-stage pressure-bearing groove is larger than that of the second outlet <NUM>. The first multi-stage pressure-bearing groove and the second multi-stage pressure-bearing groove are respectively recessed on the two parallel sides of the slipper <NUM> is located. Both the first multi-stage pressure-bearing groove and the second multi-stage pressure-bearing groove include a primary pressure-bearing groove and a plurality of auxiliary pressure-bearing grooves. The primary pressure-bearing groove is arranged at the center of the two parallel sides of the slipper <NUM>. The first outlet <NUM> is arranged at the bottom of the primary pressure-bearing groove such that the first liquid flow channel <NUM> is communicated with the first multi-stage pressure-bearing groove. The second outlet <NUM> is arranged at the bottom of the primary pressure-bearing groove such that the second liquid flow channel <NUM> is communicated with the second multi-stage pressure-bearing groove. The plurality of auxiliary pressure-bearing grooves are arranged around the outer circumference of the basic pressure-bearing groove in sequence. The high-pressure liquid in the primary pressure-bearing groove bears the main hydraulic pressure, and passes through the gap between the surface of the slipper liner <NUM> and one of the two parallel sides of the slipper <NUM> to partially overflow and leak into the adjacent auxiliary pressure-bearing grooves. The high-pressure liquid in the plurality of auxiliary pressure-bearing grooves also plays a role of static pressure support for the slipper <NUM>, increasing the supporting area, and partially overflows and leaks into the adjacent auxiliary pressure-bearing grooves. The pressure and the amount of the liquid in the multi-stage pressure-bearing groove gradually decreases, from the basic pressure-bearing groove outwards to the plurality of auxiliary pressure-bearing groove. The usage of the multi-stage pressure-bearing groove has the following advantages. The pressure of the basic pressure-bearing groove located in the center of the ring is maximized. The liquid flow introduced from the high-pressure working chamber is effectively used. The liquid static pressure supporting force is stable and evenly distributed, and the static pressure support effect is better.

As shown in <FIG>, the first multi-stage pressure-bearing groove and the second multi-stage pressure-bearing groove are independently rectangular. The first multi-stage pressure-bearing groove is the first multi-stage rectangular groove <NUM>, which includes a first rectangular primary pressure-bearing groove <NUM> arranged at the center of one of the two parallel sides of the slipper <NUM> and a first rectangular auxiliary pressure-bearing groove <NUM> arranged around the outer circumference of the first rectangular primary pressure-bearing groove <NUM>. The second multi-stage pressure-bearing groove is the second multi-stage rectangular groove <NUM>, which includes a second rectangular primary pressure-bearing groove <NUM> arranged at the center of one of the two parallel sides of the slipper <NUM> and a second rectangular auxiliary pressure-bearing groove <NUM> arranged around the outer circumference of the second rectangular primary pressure-bearing groove <NUM>. The first multi-stage rectangular groove <NUM> and the second multi-stage rectangular groove <NUM> are respectively arranged on the two parallel sides of the slipper <NUM>. The first liquid flow channel outlet <NUM> is arranged at the bottom of the first rectangular primary pressure-bearing groove <NUM> of the first multi-stage rectangular groove <NUM> such that the first multi-stage rectangular groove <NUM> is communicated with the first liquid flow channel <NUM>. The second outlet <NUM> is arranged at the bottom of the second rectangular primary pressure-bearing groove <NUM> of the second multi-stage rectangular groove <NUM> such that the second multi-stage rectangular groove <NUM> is communicated with the second liquid flow channel <NUM>.

As shown in <FIG>, the first multi-stage pressure-bearing groove and the second multi-stage pressure-bearing groove are independently circular. The first multi-stage pressure-bearing groove is the first multi-stage circular groove <NUM>, which includes a first circular primary pressure-bearing groove <NUM> arranged at the center of one of the two parallel sides of the slipper <NUM>, and a first circular auxiliary pressure-bearing groove <NUM> arranged around the outer circumference of the first circular primary pressure-bearing groove <NUM>. The second multi-stage pressure-bearing groove is a second multi-stage circular groove <NUM>, which includes a second circular primary pressure-bearing groove <NUM> arranged at the center of one of the two parallel sides of the slipper <NUM>, and a second circular auxiliary pressure-bearing groove <NUM> arranged around the outer circumference of the second circular primary pressure-bearing groove <NUM>. The first multi-stage circular groove <NUM> and the second multi-stage circular groove <NUM> are respectively arranged on the two parallel sides of the slipper <NUM>. The first outlet <NUM> is arranged at the bottom of the first circular primary pressure-bearing groove <NUM> of the first multi-stage circular groove <NUM> such that the first multi-stage circular groove <NUM> is communicated with the first liquid flow channel <NUM>. The second outlet <NUM> is arranged at the bottom of the second circular primary pressure-bearing groove <NUM> of the second multi-stage circular groove <NUM> such that the second multi-stage circular groove <NUM> is communicated with the second liquid flow channel <NUM>.

To simplify the processing, the first liquid flow channel <NUM> and the second liquid flow channel <NUM> both can be combined by several straight channels when processing. The processing of the first liquid flow channel <NUM> is described as follows. A though hole is processed by drilling downward at a certain angle from the upper end of the rotating disc and then drilling upward at a certain angle from the lower end of the slipper <NUM>. After that, a drilling operation is performed at the bottom of the liquid pressure-bearing groove on the side of the slipper <NUM> to form the hole of the first liquid flow channel outlet <NUM>, communicated with the above-mentioned though hole. At last, the hole at the lower end of the slipper <NUM> is blocked. The processing of the second liquid flow channel <NUM> is in the same way, described as follows. A though hole is processed by drilling downward at a certain angle from the upper end of the rotating disc and then drilling upward at a certain angle from the lower end of the slipper <NUM>. After that, a drilling operation is performed at the bottom of the liquid pressure-bearing groove on the side of the slipper <NUM> to form the hole of the second outlet <NUM>, communicated with the above-mentioned though hole. At last, the hole at the lower end of the slipper <NUM> is blocked.

Claim 1:
A spherical pump, comprising:
a rotating disc (<NUM>);
a rotor; and
a hydrostatic pressure support for the rotor;
characterized in that the hydrostatic pressure support comprises:
a first liquid flow channel (<NUM>);
a second liquid flow channel (<NUM>); and
at least two pressure-bearing grooves;
wherein the first liquid flow channel (<NUM>) and the second liquid flow channel (<NUM>) are both arranged on the rotating disc (<NUM>); two parallel sides of a slipper (<NUM>) of the rotor are respectively provided with the pressure-bearing grooves; the first liquid flow channel (<NUM>) comprises a first inlet (<NUM>) and a first outlet (<NUM>); the first inlet (<NUM>) is communicated with a first working chamber of the spherical pump; the second liquid flow channel (<NUM>) comprises a second inlet (<NUM>) and a second outlet (<NUM>); the second inlet (<NUM>) is communicated with a second working chamber of the spherical pump; the first outlet (<NUM>) and the second outlet (<NUM>) are respectively communicated with the pressure-bearing grooves provided on the two parallel sides of the slipper (<NUM>); a slipper liner (<NUM>) is arranged between each of the two parallel sides of the slipper (<NUM>) and a sliding groove (<NUM>) of the spherical pump; the two parallel sides of the slipper (<NUM>) respectively fit with slipper liners (<NUM>) on both sides; the slipper (<NUM>) is configured to slide back and forth in the sliding groove (<NUM>) along surfaces of the slipper liners (<NUM>); and the hydrostatic pressure support is arranged between each of the two parallel sides of the slipper (<NUM>) and a corresponding slipper liner (<NUM>).