Bidirectional gear motor pump

Abstract

The present invention discloses a two-way gear motor pump, which includes a tooth shaft, a front cover, a pump body, a rear cover, and an internal gear ring. In addition, it further includes: an axial sealing assembly having a pair of side plates and an external oil leakage channel for circulating the hydraulic oil heated inside the pump body to flow outside the pump; the external oil leakage channel includes: a first channel formed by the gap between the front side plate of the pair of side plates, the front cover, and the tooth shaft; a second channel formed by the gap between the rear side plate of the pair of side plates, the rear cover, and the tooth shaft; a third drain channel opened on the tooth shaft and having its oil inlet connected to the first channel and its oil outlet connected to the second drain channel; and a fourth channel opened on the rear cover and having its oil inlet connected to the second channel and the third drain channel respectively. The two-way gear motor pump of the present invention can work normally under both forward and reverse rotations, has a large flow rate and a high pressure, and the heated hydraulic oil can leak outside the pump body, which is beneficial to the heat dissipation of the pump body and improves the service life of the gear motor pump.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic engineering, and particularly relates to a two-way gear motor pump. Background Art

[0002] The use of a gear pump requires connecting many accessories such as a motor, a base, and a shield. The volume of the entire structure is large. Due to the problem of the pressure relief channel setting of the gear pump, the inlet and outlet ports of the gear pump are pre-assembled before leaving the factory. Usually, it can only be used normally when the tooth shaft rotates in one direction, such as forward rotation, and cannot be used normally when rotating in the opposite direction, i.e., reverse rotation. This makes the gear pump unable to meet the needs of customers with different inlet and outlet port position requirements. Therefore, many gear pump manufacturing enterprises are committed to producing a double-rotation gear pump that can rotate in both directions and work normally.

[0003] The existing double-rotation gear pumps can be divided into the following two types. One type of gear pump has a large displacement, usually 3 - 160 ml / r, but a low pressure, usually less than 21 MPa. The other type of gear pump has a high pressure, up to 35 MPa, but a small displacement, usually less than 10 ml / r. So far, there has been no double-rotation gear pump that can meet the two requirements of large displacement and high pressure at the same time. Moreover, for the above double-rotation gear pumps, the oil circuit circulation often adopts internal circulation in the pump body. When the gear pump works, the temperature of the pump body will be high due to poor heat dissipation of the hydraulic oil, reducing the service life of the gear pump. Summary of the Invention

[0004] The purpose of the present invention is to solve the above problems, and provide a two-way gear motor pump that can work normally in both forward and reverse rotations, has a large flow rate and a high pressure, and the heated hydraulic oil can leak out of the pump body, which is beneficial to the heat dissipation of the pump body and improves the service life of the gear motor pump.

[0005] To achieve the above object of the present invention, the two-way gear motor pump of the present invention includes a tooth shaft, a front cover, a pump body, a rear cover, and an internal gear ring. In addition, it further includes: an axial sealing assembly having a pair of side plates and an external leakage oil channel for circulating the heated hydraulic oil in the pump body towards the outside of the pump body; the external leakage oil channel includes: a first channel formed by the gap between the front side plate of the pair of side plates, the front cover, and the tooth shaft; a second channel formed by the gap between the rear side plate of the pair of side plates, the rear cover, and the tooth shaft; a third leakage channel opened on the tooth shaft and having its inlet connected to the first channel and its outlet connected to the second leakage channel; a fourth channel opened on the rear cover and having its inlet connected to the second channel and the third leakage channel respectively; the fourth channel axially penetrates the rear cover along the axis of the rear cover, or extends from the center of the rear cover to the outer wall of the rear cover along the radial direction of the rear cover.

[0006] Preferably, the third channel includes a radial oil drain hole formed in the middle of the gear shaft and extending radially from its center, the oil inlet of the radial oil drain hole being formed in the outer wall of the gear shaft; and an axial oil drain hole formed in the gear shaft and extending along its axial direction, the oil inlet of which is communicated with the oil outlet of the radial oil drain hole, and the oil outlet of which is communicated with the second drain channel.

[0007] Furthermore, it further includes a radial clearance compensation assembly, which includes: an inner crescent plate extending in a crescent shape from its middle part towards both sides, wedge-shaped grooves being respectively formed in the middle parts of its front end face and rear end face; a pair of outer crescent plates arranged symmetrically on the outside of the inner crescent plate and in a crescent shape, a wedge-shaped space being formed between the opposite end faces of the pair of outer crescent plates; a pair of wedge-shaped positioning members respectively arranged in the pair of wedge-shaped grooves and the wedge-shaped space of the inner crescent plate for positioning and oil passing and pressure relief; wherein, the wedge-shaped positioning members have the same shape as the wedge-shaped grooves but have a gap.

[0008] Furthermore, the axial seal assembly further includes a pair of positioning pins installed at both ends of the pump body and respectively passing through a pair of side plates and the front cover and the rear cover, and the positioning pins are fixedly connected with the corresponding wedge-shaped positioning members or integrally formed into crescent plate positioning pins.

[0009] Preferably, the rear cover is a control rear cover with a control function or a common rear cover without a control function. A pair of overflow valve jacks and a pair of one-way valve jacks are arranged on the control rear cover, and a pair of oil passing holes symmetrically arranged about the center of the rear cover are formed on the rear end face of the pump body for connecting with the rear cover.

[0010] Preferably, the radial clearance compensation assembly further includes: a sealing rod and a sealing spring piece arranged in the space formed by the inner wall of the outer crescent plate and the outer wall of the inner crescent plate; a compensation spring piece arranged in the space formed by the inner wall of the outer crescent plate and the outer wall of the inner crescent plate.

[0011] Preferably, a first placement groove and a second placement groove located outside the first placement groove are formed in the inner side wall of the outer crescent plate. The sealing rod and the sealing spring piece are arranged in the space formed by the first placement groove and the outer wall of the inner crescent plate, and the compensation spring piece is arranged in the space formed by the second placement groove and the outer wall of the inner crescent plate.

[0012] Preferably, an anti-disengagement structure is further arranged between the outer wall of the inner crescent plate and the inner walls of the pair of outer crescent plates to prevent the pair of outer crescent plates from disengaging from the inner crescent plate.

[0013] Preferably, the anti-disengagement structure includes: a pair of hook-shaped parts arranged on the outer wall of the inner crescent plate and protruding towards the outer crescent plate on both sides of the wedge-shaped groove; anti-disengagement grooves arranged on the inner wall of each outer crescent plate and adapted to the shape of the corresponding hook-shaped parts, and the hook-shaped parts can be clamped in the anti-disengagement grooves to prevent the outer crescent plate from disengaging from the inner crescent plate.

[0014] Further, it further includes an oil drain balance channel for connecting the first channel and the second channel to keep the oil pressure balanced between the front cover and the rear cover.

[0015] Preferably, the oil drain balance channel includes a pair of arc-shaped grooves provided at the bottoms of a pair of hook-shaped portions of the inner crescent plate and penetrating the front end face and the rear end face of the inner crescent plate.

[0016] Preferably, the pair of arc-shaped grooves are provided at positions close to the wedge-shaped groove at the bottoms of the pair of hook-shaped portions.

[0017] Preferably, a pair of oil ports with equal diameters and communicating with the inner cavity of the pump body are provided on both sides of the pump body, and each oil port can be used as an oil inlet and an oil outlet respectively.

[0018] Preferably, a plurality of anti-friction oil grooves for balancing the pressure on the internal gear ring are provided on the inner hole wall of the pump body.

[0019] Preferably, the anti-friction oil grooves are annularly arranged on the inner hole wall of the pump body.

[0020] Preferably, the anti-friction oil grooves are V-shaped.

[0021] Further, the axial sealing assembly further includes: two groups of sealing retaining rings corresponding to and contacting a pair of side plates, each group of sealing retaining rings includes a pair of sealing retaining rings, and a clamping groove is provided on the outer periphery of each sealing retaining ring; a plurality of sealing rings sleeved on the clamping grooves of the plurality of sealing retaining rings.

[0022] Preferably, a pair of symmetrically arranged sealing retaining ring grooves are respectively provided on the end faces of the front cover and the rear cover facing the pump body.

[0023] Preferably, a pair of oil through holes symmetrically centered on the rear cover are provided on the rear end face of the pump body for connecting with the rear cover.

[0024] Preferably, a shaft hole for arranging the rear end of the tooth shaft is further provided on the front end face of the rear cover, and the shaft hole communicates with the fourth channel.

[0025] Preferably, the rear cover is a control rear cover with a control function or a common rear cover without a control function.

[0026] Preferably, the control rear cover is further provided with a pair of overflow valve holes and a pair of one-way valve holes.

[0027] Further, a heat dissipation groove for heat dissipation is provided on the rear end face of the rear cover.

[0028] Preferably, the heat dissipation groove includes a plurality of longitudinal grooves and a plurality of transverse grooves, and the plurality of longitudinal grooves and the plurality of transverse grooves intersect with each other.

[0029] Compared with the prior art, the bidirectional gear motor pump of the present invention has the following beneficial effects:

[0030] 1. The bidirectional gear motor pump of the present invention has an external leakage oil passage. When the bidirectional gear motor pump is working, the hydraulic oil carrying heat is quickly discharged through the external leakage oil passage, so that the heat generated during the operation of the fluid machine is quickly dissipated, reducing the adverse effect of heat on the temperature rise of the pump body, and improving the working performance and service life of the bidirectional gear motor pump.

[0031] 2. For the bidirectional gear motor pump of the present invention, the rear cover of the pump body can be a common rear cover or a control rear cover. Therefore, the bidirectional gear motor pump of the present invention can be applied to both conventional hydraulic systems and closed-loop hydraulic systems, improving its scope of application, meeting different usage requirements of customers, and greatly reducing the difficulty of inventory management of manufacturers, reducing inventory and assembly costs, and on this premise, greatly reducing the customer customization cost.

[0032] The present invention will be described in detail below with reference to the accompanying drawings. Description of the Drawings

[0033] Figure 1 is a perspective view of the bidirectional gear motor pump according to the first embodiment of the present invention;

[0034] Figure 2 is a front view of the bidirectional gear motor pump according to the first embodiment of the present invention;

[0035] Figure 3 is a half-sectional view of the bidirectional gear motor pump according to the first embodiment of the present invention;

[0036] Figure 4 is Figure 3 the view in the direction of A-A in

[0037] Figure 5a is a perspective view of one perspective of the support cover of the present invention;

[0038] Figure 5b is a perspective view of another perspective of the support cover of the present invention;

[0039] Figure 5c is a front view of the support cover of the present invention;

[0040] Figure 5d is a rear view of the support cover of the present invention;

[0041] Figure 6 is a perspective view of the first perspective of the pump body of the present invention;

[0042] Figure 7 is a perspective view of the second perspective of the pump body of the present invention;

[0043] Figure 8It is a perspective view of the rear cover of the present invention from the first perspective;

[0044] Figure 9 It is a perspective view of the rear cover of the present invention from the second perspective;

[0045] Figure 10 It is a perspective view of the gear shaft of the present invention;

[0046] Figure 11 It is a perspective view of the clearance compensation component and the rear side plate of the present invention in cooperation from the first perspective;

[0047] Figure 12 It is a perspective view of the clearance compensation component of the present invention with the outer crescent plate removed;

[0048] Figure 13 It is a sectional view of the internal gear ring, the clearance compensation component and the gear shaft of the present invention in cooperation;

[0049] Figure 14 It is a perspective view of the crescent plate positioning pin of the present invention;

[0050] Figure 15a It is a perspective view of the inner crescent plate of the present invention;

[0051] Figure 15b It is a front view of the inner crescent plate of the present invention;

[0052] Figure 16a It is a perspective view of the outer crescent plate of the present invention;

[0053] Figure 16b It is a front view of the outer crescent plate of the present invention;

[0054] Figure 17 It is a perspective view of the special-shaped sealing retaining ring of the present invention;

[0055] Figure 18 It is a perspective view of the special-shaped sealing ring of the present invention;

[0056] Figure 19 It is a perspective view of the sealing spring piece of the present invention;

[0057] Figure 20 It is a perspective view of the compensation spring piece of the present invention;

[0058] Figure 21 It is an exploded view of a part of the axial sealing component and the internal gear ring of the present invention;

[0059] Figure 22a It is a perspective view of the rear side plate of the present invention;

[0060] Figure 22b It is a relative position diagram of the rear side plate and the sealing retaining ring of the present invention;

[0061] Figure 23It is a perspective view of the control rear cover of the present invention from the first perspective;

[0062] Figure 24 It is a perspective view of the control rear cover of the present invention from the second perspective;

[0063] Figure 25 It is a perspective view of the control rear cover of the present invention from the third perspective;

[0064] Figure 26 It is a front view of the valve body of the control rear cover of the present invention;

[0065] Figure 27 It is a bottom view of the valve body of the present invention;

[0066] Figure 28 It is a right view of the valve body of the present invention;

[0067] Figure 29 It is a left view of the valve body of the present invention;

[0068] Figure 30 It is a rear view of the valve body of the present invention;

[0069] Figure 31 It is Figure 26 A sectional view of the valve body in the B - B direction;

[0070] Figure 32 It is Figure 29 A sectional view of the valve body in the C - C direction;

[0071] Figure 33 It is Figure 30 A sectional view of the valve body in the D - D direction;

[0072] Figure 34 It is Figure 30 A sectional view of the valve body in the E - E direction;

[0073] Figure 35 It is Figure 26 A sectional view of the valve body in the F - F direction;

[0074] Figure 36 It is a schematic diagram of the external leakage oil passage of the present invention (the external leakage oil holes forming the fourth passage are not shown);

[0075] Figure 37 It is a perspective view of the two - way gear motor pump according to the second embodiment of the present invention;

[0076] Figure 38 It is a rear end face view of the rear cover of the two - way gear motor pump according to the third embodiment of the present invention;

[0077] Figure 39 It is another schematic diagram of the sealing structure in the two - way gear motor pump of the present invention;

[0078] Figure 40 It isFigure 39 Front view of the middle sealing structure;

[0079] Figure 41 is Figure 40 View G-G of the middle sealing structure. Detailed implementation mode

[0080] As Figures 1-4 shown, they are respectively schematic diagrams of each structure under the first structure of the two-way gear motor pump of the present invention. As Figure 37 shown, it is a perspective view of the second structure of the two-way gear motor pump of the present invention. It can be seen from the figure that the two-way gear motor pump of the present invention includes a tooth shaft 1, a front cover, a pump body 10, a rear cover 14, and an internal gear ring 9. In addition, it further includes: an axial sealing assembly having a pair of side plates and an external leakage oil passage for circulating the hydraulic oil that becomes hot inside the pump body 10 to the outside of the pump body 10; the external leakage oil passage includes: a first passage formed by the gap between the front side plate 8 of the pair of side plates, the front cover, and the tooth shaft 1; a second passage formed by the gap between the rear side plate 18 of the pair of side plates, the rear cover 14, and the tooth shaft 1; a third leakage passage opened on the tooth shaft 1 and having an oil inlet connected to the first passage and an oil outlet connected to the second leakage passage; a fourth passage opened on the rear cover 14 and having an oil inlet connected to the second passage and the third leakage passage respectively; the fourth passage axially penetrates the rear cover 14 along the axis of the rear cover 14, or extends from the center of the rear cover 14 to the outer wall of the rear cover 14 along the radial direction of the rear cover 14.

[0081] When the two-way gear motor pump of the present invention is working, the lubricating oil and hydraulic oil leaked inside during the working process of the motor pump are quickly leaked to the outside through the external leakage oil passage, so that the heat generated during the operation of the fluid machine is quickly dissipated, reducing the adverse effect of the heat on the temperature rise of the pump body, and improving the working performance and service life of the two-way gear motor pump.

[0082] Among them, the rear cover 14 of the present invention can adopt a common rear cover, such as Figures 1-4 , Figure 8 , Figure 9 shown, or it can also adopt a control rear cover as shown in Figure 37 , Figures 23-25 shown. Thus, the two-way gear motor pump of the present invention can be applied to both conventional hydraulic systems and closed-loop hydraulic systems, improving its applicable range, meeting different usage requirements of customers, and greatly reducing the difficulty of inventory management of manufacturers, reducing inventory and assembly costs, and on this premise, greatly reducing the customization cost of customers.

[0083] Next, in combination with specific embodiments, the structure of the two-way gear motor pump of the present invention will be described in detail.

[0084] Embodiment 1

[0085] AsFigures 1-4 As shown in the figure, it is a schematic diagram of the structures of the first structure of the two-way gear motor pump of the present invention. It can be seen from the figure that the two-way gear motor pump of this embodiment includes: a tooth shaft 1 with an external gear; a pump body 10 sleeved on the tooth shaft 1; a support cover 6 sleeved on the tooth shaft 1 and located at the front end of the pump body 10, and a flange front cover 5 located at the front end of the support cover 6. The flange front cover 5 and the support cover 6 form a front cover, and the front end of the tooth shaft 1 extends out of the flange front cover 5; a rear cover 14 installed at the rear end of the pump body 10; a shaft head oil seal 2, a snap ring 3, and an O-ring 4 installed inside the flange front cover 5, and a sliding bearing 17 installed at the rear end of the tooth shaft 1 extending into the rear cover 14; an internal gear ring 9 meshing with the external gear of the tooth shaft 1. Among them, the center of the tooth shaft 1 and the center of the internal gear ring 9 are eccentrically arranged. The external gear of the tooth shaft 1 meshes with the internal teeth of the internal gear ring 9, and the tooth shaft 1 can freely float and rotate in the internal gear ring 9; a radial clearance compensation component provided between the external gear of the tooth shaft 1 and the internal gear ring 9; an axial seal component provided on both sides after the internal gear ring 9 and the external gear of the tooth shaft 1 are assembled. The axial seal component respectively has side plates, including a front side plate 8 and a rear side plate 18; an external leakage oil passage provided on the two-way gear motor pump; in addition, it also includes an internal hydraulic oil circulation passage, and the internal hydraulic oil circulation passage can adopt a conventional set passage, which will not be described in detail here.

[0086] In this embodiment, the front cover, the pump body 10 and the rear cover 14 are connected together by bolts and flat washers. The bolts and flat washers are matched and there are multiple of each, for example, 4 can be used respectively. The rear cover 14 of this embodiment is a common rear cover, that is, a rear cover without hydraulic valves such as overflow valves and check valves. The two-way gear motor pump of this embodiment can be applied to a conventional hydraulic system. During manufacturing, the flange front cover 5 and the support cover 6 can be integrally formed, or can be separately formed and then assembled together. When separately formed, the structure of the flange front cover 5 can be determined according to customer requirements such as installation of a stop and matching of a transmission shaft. Hereinafter, only the structure in which the flange front cover 5 and the support cover 6 are separately formed and then assembled together will be described.

[0087] Among them, in order to enable the heat carried by the hydraulic oil in the pump body to be quickly dissipated when the two-way gear motor pump of this embodiment works, so as to reduce the adverse impact of heat on the temperature rise of the pump body and improve the working performance and service life of the two-way gear motor pump, this embodiment adopts an external leakage oil passage that can make the heated hydraulic oil in the pump body 10 circulate outward from the pump body 10, so as to quickly discharge the hot hydraulic oil outside the pump body 10, and then through a pipeline, the hydraulic oil discharged outside the pump body 10.

[0088] Such as Figure 36As shown in the figure, the external leakage oil passage of this embodiment includes: a first passage formed by the gap between the front side plate 8 of a pair of side plates, the support cover 6, and the gear shaft 1; a second passage formed by the gap between the rear side plate 18 of a pair of side plates, the rear cover 14, and the gear shaft 1; a third drain passage opened on the gear shaft 1, with its oil inlet communicating with the first passage and its oil outlet communicating with the second drain passage; and a fourth passage opened on the rear cover 14, with its oil inlet communicating with the second passage and the third drain passage respectively.

[0089] Among them, as Figure 10 shown, the third passage includes: a radial drain hole 1a opened in the middle of the gear shaft 1 and extending radially from its center. The oil inlet of the radial drain hole 1a is located on the outer wall of the gear shaft 1, and the oil inlet is opened on the part of the gear shaft 1 between the shaft head oil seal 2 and the flange front cover 5; an axial drain hole 1b opened in the center of the gear shaft 1 and extending along its axis. Its oil inlet is connected to the oil outlet of the radial drain hole, and its oil outlet is located at the rear end face of the gear shaft 1 and is connected to the second drain passage. The radial drain hole 1a and the axial drain hole 1b are vertically connected, and the radial drain hole 1a and the axial drain hole 1b are respectively circular drain holes.

[0090] Among them, during design, the fourth passage can penetrate the rear cover 14 axially along the rear cover 14 (as Figure 8 , Figure 9 shown), that is, an external leakage oil hole 141 for forming the fourth passage is opened in the center of the rear cover 14. The external opening of the external leakage oil hole 141 is located on the outer wall of the rear cover 5, and the internal opening is connected to the shaft hole 142 opened on the rear cover 14. Or, the external leakage oil hole can also extend from the shaft hole 142 on the rear cover 14 to the outer wall of the rear cover 14 radially (as shown by the dotted arrow in Figure 36 ), and this external leakage oil hole is connected to the end of the shaft hole on the rear cover to drain the hydraulic oil radially. During manufacturing, a radially extending external leakage oil hole and an axially extending external leakage oil hole can be machined on the rear cover 14 at the same time, and both external leakage oil holes are blocked with removable sealing plugs (not shown in the figure, and the existing technology sealing plug structure can be used). When connecting the motor pump to other equipment, the sealing plug of one of the external leakage oil holes can be removed as needed to use this external leakage oil hole as the fourth passage for draining oil. By using this method, the motor pump can have a wider application range.

[0091] The oil groove 607 on the support cover 6 communicates with the radial oil drain hole 1a, and the axial oil drain hole 1b communicates with the shaft hole 142 and the external oil drain hole 141, so that the four channels are connected to form a path for the hydraulic oil to circulate outward, enabling the lubricating oil and hydraulic oil leaked internally during the operation of the motor pump (such as the leakage from the gaps between the following axial clearance compensation components, radial clearance compensation components and the pump body, etc.) to flow outside the pump body, reducing the influence of heat on the temperature rise of the pump body, effectively reducing the temperature of the pump body, and having better heat dissipation performance.

[0092] Among them, as Figure 1 shown, a pair of mounting spigots are symmetrically arranged on the flange front cover 5 of this embodiment to facilitate the installation of the fluid machine on the supporting equipment. The support cover 6 is waist-shaped (as Figures 5a-5d shown), its front end face is used to connect with the rear end face of the flange front cover 5, and its rear end face is used to connect with the front end face of the pump body 10. As Figure 5a 、 Figure 5c shown, a circular boss concentric with the center of the support cover 6 is provided on the rear end face of the support cover 6, and the following holes and grooves are provided on the circular boss: a shaft hole 601 eccentric to the circular boss and axially penetrating the thickness of the support cover 6 for the tooth shaft 1 to pass through, a pair of seal retaining ring grooves 605 symmetrically arranged on both sides of the shaft hole 601, each seal retaining ring groove is used to place a seal retaining ring, the depth of the seal retaining ring groove 605 is less than the thickness of the circular boss, a crescent plate positioning pin insertion hole 604 located between the pair of seal retaining ring grooves 605, and this insertion hole is a blind hole. In addition, a positioning pin hole 603 located outside the circular boss is also provided on the rear end face of the support cover 6, and this positioning pin hole 603 is a blind hole, and a positioning pin for connecting the pump body 10 and the support cover 6 is inserted therein.

[0093] As Figure 5b 、 Figure 5d shown, a circular boss 606 eccentric to the center of the support cover 6 is provided on the front end face of the support cover 6, this circular boss 606 is concentric with the shaft hole 601, and an oil groove 607 concentric with the shaft hole 601, having a diameter larger than the shaft hole 601 and communicating with the shaft hole 601 is provided at the center of the circular boss 606. The tooth shaft 1 passes through the oil groove 607, the shaft head oil seal 2 and the snap ring 3 are both placed in the oil groove 607, a seal ring groove is provided around the outer circumference of the circular boss 606, and an O-ring seal 4 is placed in the seal ring groove to seal the flange front cover 5 and the support cover 6 during assembly. In addition, four screw holes for bolts to pass through are also provided on the support cover 6 and penetrate its thickness.

[0094] The outer shape of the pump body 10 in this embodiment is square, and a pair of opposite surfaces are flat, and the other pair of opposite surfaces are of special-shaped arcs (as Figure 1 、 Figure 6 、 Figure 7As shown, in addition, the outer shape of the pump body 10 can also be other shapes, as long as it can be adapted to the front cover and the rear cover (not shown in the figure).

[0095] As Figure 6 , Figure 7 shown, the pump body 10 is hollow to form an inner cavity for arranging the internal gear ring 9, the radial clearance compensation component, and the outer gear portion of the gear shaft 1 therein. On both sides of the pump body 10, there are a pair of oil ports with equal diameters and communicating with the inner cavity of the pump body 10, that is, the first oil port 101 and the second oil port 107. The outer openings of the pair of oil ports are respectively located on the outer walls of a pair of opposite surfaces of the pump body 10 that are flat. Each oil port can serve as an oil inlet and an oil outlet respectively. That is, when the gear motor pump of the present invention rotates forward, one of the oil ports, such as the first oil port 101, can be used as the oil inlet, and the other oil port, such as the second oil port 107, can be used as the oil outlet. When the gear motor pump rotates in reverse, the first oil port 101 can be used as the oil outlet, and the second oil port 107 can be used as the oil inlet. Since the diameters of the two oil ports are equal, the same displacement and pressure can be achieved whether the gear motor pump rotates forward or in reverse.

[0096] Among them, in addition to opening two oil ports on the opposite outer walls of the pump body 10, a shaft hole for the gear shaft 1 to pass through is also opened at the center of the pump body 10 through the thickness of the pump body 10. In addition, on the rear end face of the pump body 10 (as Figure 6 shown) and the front end face (as Figure 7 shown), the following holes with axes parallel to the axis of the shaft hole are respectively opened: four screw holes 104 passing through the thickness of the pump body 10 and located around the shaft hole on the rear end face of the pump body 10; a pair of oil through holes 102 and 106 symmetrically arranged on both sides of the shaft hole. The pair of oil through holes are blind holes and are arranged adjacent to the outer walls of the pump body 10 with opposite surfaces being flat. The ends of the pair of oil through holes can be correspondingly communicated with the pair of oil ports; a positioning pin hole 103 opened on the rear end face of the pump body 10 and located between the oil through hole 102 and the screw hole 104. The positioning pin hole 103 is also a blind hole and is used for inserting and connecting the positioning pin between the pump body 10 and the rear cover 14; a positioning pin hole 109 opened on the front end face of the pump body 10. The positioning pin hole 109 is a blind hole and is used for inserting and connecting the positioning pin between the pump body 10 and the support cover 6. It should be noted that since the fluid machine of this embodiment uses a common rear cover, the pair of oil through holes 102 and 106 are blocked with a sealing material, so that the pair of oil through holes cannot be communicated with the pair of oil ports.

[0097] In addition, a pair of cavity grooves 105 are also provided on the inner hole wall of the pump body 10 (i.e., the hole wall of the shaft hole). The pair of cavity grooves 105 are separated by a partition. The pair of cavity grooves 105 are located on one side of the inner hole wall of the pump body 10 and are respectively communicated with a pair of oil ports. That is, one cavity groove is communicated with the first oil port, and the other cavity groove is communicated with the second oil port. Thus, when the fluid machine works, a low-pressure cavity communicated with the oil inlet and a high-pressure cavity communicated with the oil outlet can be formed in the fluid machine. On both sides of the cavity groove 105, a plurality of anti-friction oil grooves 108 are respectively provided for balancing the pressure of the hydraulic oil in the cavity groove 105 on the internal gear ring 9 when the fluid machine works. The anti-friction oil grooves 108 are arranged in a ring shape on the inner hole wall of the pump body 10. Preferably, the anti-friction oil grooves are V-shaped, that is, the opening is wide and the bottom is narrow. The V-shaped anti-friction oil grooves can accommodate a certain amount of hydraulic oil. When the fluid machine works, there will be sliding friction between the internal gear ring 9 and the pump body 10. During this process, the hydraulic oil can fully lubricate the internal gear ring 9, reduce and compensate for the oil leakage inside the fluid machine, enable the fluid machine to maintain a preset flow rate under high pressure, and improve the efficiency of the fluid machine.

[0098] Among them, in this embodiment, the internal gear ring 9 is arranged in the pump body 10, and it adopts a cylindrical structure as shown in Figure 21 . Its interior is hollow and the inner wall is provided with teeth. A plurality of oil through holes 91 are arranged along its circumferential direction. Through these oil through holes 91, the low-pressure oil introduced as the oil inlet is introduced into the pump body, or the high-pressure oil is communicated with the oil discharge port.

[0099] The rear cover 14 connected to the rear end face of the pump body 10 in this embodiment adopts the rear cover 14 as shown in Figure 8 、 Figure 9 . The rear cover 14 is an ordinary rear cover, that is, a rear cover without any hydraulic valves. The shape of the rear cover is adapted to the shape of the pump body 10, and it is also a square-like shape with a pair of opposite faces being flat and a pair of opposite faces being arc-shaped. A circular boss concentric with its center is provided on the front end face of the rear cover 14. A shaft hole 142 for inserting the rear end of the tooth shaft 1 is opened on the circular boss. The shaft hole 142 is a blind hole and is eccentrically arranged with respect to the center of the circular boss. A pair of seal retaining ring grooves 145, 143 are symmetrically arranged on both sides of the shaft hole 142 for arranging a pair of seal retaining rings. The pointed ends of the pair of seal retaining ring grooves 145, 143 surround the outer circumference of the shaft hole 142. A crescent plate positioning pin hole 144 is arranged in the middle near the other end of the pair of seal retaining ring grooves 145, 143. The crescent plate positioning pin hole 144 is a blind hole. In addition, 4 screw holes and a positioning pin hole 146 are provided on the part of the rear cover 14 located around the circular boss, so as to connect the pump body 10 and the rear cover 14 by passing a positioning pin through the corresponding positioning pin holes 103, 146 on both of them and play an axial positioning role. An external leakage oil hole 141 (as shown in Figure 9 ) is also opened on the rear end face of the rear cover 14, and the external leakage oil hole 141 is communicated with the shaft hole 142.

[0100] Among them, in this embodiment, a radial clearance compensation component is provided between the tooth tip circle arc surface of the external gear of the tooth shaft 1 and the tooth tip circle of the internal gear ring 9 to isolate the inner cavity of the pump into a low-pressure cavity and a high-pressure cavity, and serve as the radial support between the tooth shaft 1 and the internal gear ring 9 to prevent the hydraulic oil in the fluid machine from leaking radially.

[0101] In order to enable the fluid machine of this embodiment to achieve bidirectional rotation and work with the same flow rate and the same pressure, that is, regardless of whether the tooth shaft 1 rotates forward or backward, the radial clearance compensation component can provide radial support for the tooth shaft 1 and the internal gear ring 9 and prevent the hydraulic oil in the fluid machine from leaking radially. The radial clearance compensation component of this embodiment adopts the following structure, as Figures 2-4 、 Figures 11-13 shown, which includes: an inner crescent plate 12 extending in a crescent shape from its middle part to both sides, and wedge-shaped grooves 122 are respectively opened in the middle parts of its front end face and rear end face; a pair of outer crescent plates 11 arranged symmetrically on the outside of the inner crescent plate 12 and in a crescent shape, and a wedge-shaped space is formed between the opposite end faces of the pair of outer crescent plates 11; a pair of wedge-shaped positioning members 131 respectively arranged in the pair of wedge-shaped grooves 122 and the wedge-shaped space of the inner crescent plate 12 and used for positioning and oil passage and pressure relief; among them, the wedge-shaped positioning member 131 has the same shape as the wedge-shaped groove but has a gap. In addition, it also includes: a sealing rod 21 and a sealing spring piece 22 arranged in the space formed by the inner wall of the outer crescent plate 11 and the outer wall of the inner crescent plate 12; a compensation spring piece 23 arranged in the space formed by the inner wall of the outer crescent plate 11 and the outer wall of the inner crescent plate 12.

[0102] Specifically, the inner crescent plate 12 of this embodiment adopts an arc structure as Figure 15a 、 Figure 15b shown, extending in a crescent shape from its middle part to both sides, and wedge-shaped grooves 122 are symmetrically opened in the middle parts of its front end face (the front end face refers to the end face facing the support cover 6) and rear end face (the rear end face refers to the end face facing the rear cover), and a pair of wedge-shaped grooves 122 respectively extend along the axial direction parallel to the central axis of the inner crescent plate 12, and the opening of the wedge-shaped groove 122 on the inner side wall of the inner crescent plate 12 is smaller than the opening on the outer side wall of the inner crescent plate 12, that is, the wedge-shaped groove 122 is in a state where the groove width gradually narrows from the outer side wall to the inner side wall of the inner crescent plate 12. Hydraulic oil passage grooves 124 are respectively opened on both sides of the inner crescent plate 12 where the wedge-shaped grooves 122 are located, and a pair of hydraulic oil passage grooves 124 extend along the circumferential direction of the outer wall of the inner crescent plate 12. During design, the curvature radius of the arc surface on the inner side wall of the inner crescent plate 12 is the same as that of the tooth tip circle of the tooth shaft 1.

[0103] In this embodiment, a pair of outer crescent plates 11 are symmetrically arranged on both sides of the outer side wall of the inner crescent plate 12, and the pair of outer crescent plates 11 have the same structure and both adopt the structure as Figure 16a 、 Figure 16bThe crescent-shaped structure with one thick end and one thin end is shown. The thick ends of a pair of outer crescent plates 11 are arranged facing each other. During design, the curvature radius of the arc surface on the outer side of the outer crescent plate 11 is the same as that of the addendum circle of the internal gear ring 9, while the curvature radius of the arc surface on the inner side thereof is the same as that of the outer side wall of the inner crescent plate.

[0104] On the inner side wall of the outer crescent plate 11, a first placement groove 112 and a second placement groove 113 located outside the first placement groove 112 are provided. The sealing rod 21 and the sealing spring piece 22 are placed in the space between the first placement groove 112 and the corresponding outer wall of the inner crescent plate 12, and the compensation spring piece 23 is placed in the space between the second placement groove 113 and the corresponding outer wall of the inner crescent plate 12.

[0105] The gap between the inner and outer crescent plates is filled by the sealing rod 21 and the sealing spring piece 22. The sealing rod 21 is a circular and elastic sealing rod, which has a certain telescopic function, while the sealing spring piece 22 adopts a shape such as Figure 19 shown, with a concave middle and convex sides. During use, the sealing rod 21 and the sealing spring piece 22 can automatically adjust the contraction amount according to the different working states of the fluid machine, so as to better match the gap between the inner and outer crescent plates. And the compensation spring piece 23 adopts a spring piece such as Figure 20 shown, with a slightly convex arc. Its convex part faces the outer crescent plate, which can provide radial support for the inner and outer crescent plates, fix the inner and outer crescent plates radially between the tooth shaft 1 and the addendum circle of the internal gear ring 9, and always has the tendency to make the inner and outer crescent plates closely adhere to the tooth shaft 1 and the internal gear ring 9 respectively, so as to compress the sealing rod 21, so that the hydraulic oil between the gaps of the inner and outer tooth plates can be sealed through the sealing rod 21.

[0106] Whether the hydraulic oil pressure in the fluid machine is very low or after the hydraulic oil pressure is established, due to the elastic forces given by the sealing rod 21, the sealing spring piece 22, and the compensation spring piece 23, the inner and outer crescent plates can be respectively opened and closely adhere to the inner addendum circle of the tooth shaft 1 and the internal gear ring 9, so that the outer cylindrical surface of the floating internal gear ring 9 tightly seals the oil outlet of the pump body 10, so that the low-pressure chamber and the high-pressure chamber are completely isolated. It can be seen that the radial clearance compensation component has good structural stability. The three components cooperate with each other to complete the sealing and clearance adjustment, with better effects, which can greatly reduce the possibility of hydraulic oil leakage along the radial or axial direction, make the working performance of the fluid machine more reliable, and improve the volumetric efficiency of the fluid machine. In addition, the sealing rod 21 and the sealing spring piece 22 in this embodiment can also adopt a triangular rod with two sides in the prior art.

[0107] Since in this embodiment, a structure is adopted in which an outer crescent plate is respectively arranged on both sides of the outer side wall of an inner crescent plate so that the gear motor pump can rotate bidirectionally. That is, regardless of whether the gear motor pump is working forward or backward, only one outer crescent plate, a set of sealing rods 21, sealing spring pieces 22, and compensation spring pieces 23 at the position corresponding to the outer crescent plate and the inner crescent plate cooperate with each other to completely isolate the low-pressure chamber and the high-pressure chamber of the fluid machine and prevent hydraulic oil from leaking radially or axially. In order to prevent the other outer crescent plate from detaching from the inner crescent plate when one outer crescent plate cooperates with the inner crescent plate, etc., this embodiment also provides an anti-detachment structure between the outer wall of the inner crescent plate 12 and the inner walls of a pair of outer crescent plates 11.

[0108] Specifically, as Figures 11-16b shown, the anti-detachment structure of this embodiment includes: a pair of hook-shaped portions 123 protruding toward the outer crescent plate 11 and arranged on the outer wall of the inner crescent plate 12 and on both sides of the wedge-shaped groove 122; anti-detachment grooves 111 arranged on the inner walls of each outer crescent plate 11 and adapted to the shape of the corresponding hook-shaped portion 123. The hook-shaped portion 123 can be clamped in the anti-detachment groove 111 to prevent the outer crescent plate 11 from detaching from the inner crescent plate 12. In addition, a pair of arc-shaped grooves 121 penetrating the front end face and the rear end face of the inner crescent plate 12 are arranged at the bottom of a pair of hook-shaped portions 123 of the inner crescent plate 12, and the pair of arc-shaped grooves 121 are arranged at positions close to the wedge-shaped groove 122 at the bottom of the pair of hook-shaped portions 123.

[0109] A wedge-shaped space is formed between the opposite end faces of a pair of outer crescent plates 11. To prevent the pair of outer crescent plates 11 from moving circumferentially along the inner crescent plate 12 or radially along the tooth axis and changing their relative positions with respect to the inner crescent plate 12, this embodiment arranges a pair of wedge-shaped positioning members 131 for positioning and oil-passing pressure relief in the pair of wedge-shaped spaces formed by the pair of wedge-shaped grooves 122 of the inner crescent plate 12 and the opposite end faces of the pair of outer crescent plates 11. The wedge-shaped positioning member 131 adopts a wedge shape as Figure 14 shown, that is, the upper surface and the lower surface of the wedge-shaped positioning member 131 are both arc-shaped surfaces (which can also be flat surfaces), and the arc length of the upper arc-shaped surface is greater than the arc length of the lower arc-shaped surface. The two sides of the upper and lower arc-shaped surfaces are each connected by a flat surface. One wedge-shaped positioning member 131 is correspondingly arranged in one wedge-shaped groove 122, and has the same shape as the wedge-shaped groove 122 but a width dimension slightly smaller than that of the wedge-shaped groove 122, so that there will be a certain gap between the side walls of the wedge-shaped positioning member 131 and the wedge-shaped groove 122 when the wedge-shaped positioning member 131 is arranged in the wedge-shaped groove 122 (as Figure 13 shown) for facilitating oil-passing pressure relief.

[0110] The wedge-shaped positioning member 131 of this embodiment is placed in the wedge-shaped groove 122 of the inner crescent plate 12 and has a gap. When the inner crescent plate and the wedge-shaped positioning member produce a cutting angle due to the operation of the fluid machine, the wedge-shaped positioning member will not separate from the wedge-shaped groove of the inner crescent plate, so that the inner arc of the inner crescent plate can support the tooth top of the gear shaft when it cooperates with the gear shaft, thereby avoiding oil leakage from the tooth top.

[0111] In addition, when an outer crescent plate plays a role in radial clearance compensation, the outer side wall of the outer crescent plate presses against the top circle of the inner gear ring, and the inner side wall presses against the gear shaft. The end surface of the outer crescent plate opposite to the other outer crescent plate can press against the side wall of the wedge-shaped positioning piece, thereby playing a sealing role. The other outer crescent plate that does not participate in the radial clearance compensation will be blocked by the wedge-shaped positioning piece and hooked by the anti-slip structure without causing circumferential displacement relative to the inner crescent plate, that is, the outer crescent plate will not fall out due to the reverse rotation of the gear shaft.

[0112] Furthermore, when the high-pressure hydraulic oil pushes the sealing rod to increase the gap between the inner and outer crescent plates to form an oblique angle, the two side surfaces of the wedge-shaped positioning member 131 will fit tightly with the wall of the wedge-shaped groove, thereby avoiding the situation where the positioning member and the inner crescent plate are not tightly fitted and the trapped oil impacts the crescent plate when a circular positioning member is used, causing the entire fluid machine to shake and work unstably. In addition, the oil leakage channel of this embodiment also includes an oil leakage balance channel for connecting the first channel and the second channel to maintain oil pressure balance between the support cover 6 and the rear cover 14. The oil leakage balance channel is formed by the above-mentioned pair of arc grooves 121 arranged at the bottom of a pair of hook-shaped portions 123 of the inner crescent plate 12 and penetrating the front end and rear end of the inner crescent plate 12. Through the oil leakage balance channel, the oil pressure balance between the support cover 6 and the rear cover 14 can be always maintained, effectively preventing the occurrence of oil entrapment between the two covers.

[0113] In this embodiment, an axial sealing assembly is further provided on both sides after the inner gear ring 9 and the outer gear of the gear shaft 1 are assembled. The axial sealing assembly includes: a front side plate 8 (such as Figure 21 The rear side plate 18 (as shown) is located between the pump body 10 and the rear cover 14 Figure 21 , Figure 22a , Figure 22b Two sets of sealing structures corresponding to the front side plate and the rear side plate are respectively in contact; a positioning pin 132 installed at the front end of the pump body 10 and passing through the front side plate 8 and inserted on the front cover (the positioning pin 132 can be as shown Figure 14 The positioning pin 132 is installed at the rear end of the pump body 10 and passes through the rear side plate 18 and is inserted into the rear cover 14. The positioning pin 132 can be used as follows Figure 14The cylindrical shape shown, and the positioning pin 132 is fixedly connected to the wedge-shaped positioning member 131 at the corresponding position to form the crescent plate positioning pin 13. During manufacturing, the positioning pin 132 and the wedge-shaped positioning member 131 can be separately formed and then connected together by welding, screwing, or bonding, or they can be integrally formed, such as using a cylindrical bar and then machined. Among them, the front side plate 8 used in conjunction with the above-mentioned sealing structure is circular, and is provided with holes as shown in Figure 21 : An axial hole 81 that penetrates its thickness and is eccentrically arranged with respect to its center is provided on the front side plate 8. On both sides of the axial hole 81, two groups of oil through holes for balancing pressure oil that penetrate the front side plate 8 are symmetrically provided. Each group of oil through holes respectively includes a circular oil through hole 83, a circular oil through hole 84, and an oblong oil through hole 85. Each group of oil through holes communicates with the corresponding sealing ring groove (such as 605 or 602) on the support cover 6. When the fluid machine works, the hydraulic oil between each oil through hole and the sealing ring groove can communicate, that is, the balancing pressure oil is connected, and the hydraulic oil supports the front side plate, so that the tooth shaft and the internal gear ring are in full and balanced contact. In addition, a crescent plate positioning pin hole 82 for the crescent plate positioning pin to pass through is provided between the two groups of oil through holes.

[0114] Among them, the structure of the rear side plate 18 is basically the same as that of the front side plate 8, that is, the rear side plate 8 is provided with an axial hole 181 with the above-mentioned functions at the corresponding position, oil through holes 183, 184, 189. The oil through holes 183 and 184 are circular oil through holes, and the oil through hole 189 is an oblong oil through hole, and a crescent plate positioning pin hole 182. In addition, a pointed angle groove 185 that communicates with the oil through holes 183 and 189 respectively is provided on the front end face of the rear side plate 18 facing the pump body 10. A notch 186 is provided at the edge of the rear side plate 18 near the crescent plate positioning pin hole 182. A fan-shaped groove 187 is opened on the front end face of the rear side plate 18. The smaller perimeter side of the fan-shaped groove 187 communicates with the axial hole 181, and the larger perimeter side of the fan-shaped groove 187 is located outside the notch 186. The pointed angle of the pointed angle groove 185 faces the fan-shaped groove 187, and the crescent plate positioning pin hole 182 is located in the fan-shaped groove 187. In addition, arc-shaped bosses 188 that protrude outward are symmetrically provided on the outer periphery of the rear side plate 18, and a pair of arc-shaped bosses 188 are respectively located on both sides of the fan-shaped groove 187.

[0115] The pointed angle groove 185 is a pressure relief groove, which is used to reduce the noise during the operation of the fluid machine. During the operation of the fluid machine, it plays a role of gradually decompressing and unloading the rotating sealing cavity, so that the pressure oil (that is, the hydraulic oil with pressure) will not suddenly open when turning to a window (that is, an oil port) and generate a large pulsation. When designing, the pointed angle groove 185 has a certain taper and length, and the taper and length can be determined according to the actual situation to better reduce the noise effect.

[0116] The notch 186 on the rear side plate 18 corresponds to the position of the partition between a pair of cavity grooves 105 in the pump body 10. A sealed or unsealed cavity can be formed between the cavity groove 105 and the internal gear ring 9. When hydraulic oil is introduced into the cavity groove and the cavity is in a sealed state, the cavity groove is a high-pressure oil groove, that is, a pressure equalizing groove. When the cavity groove is communicated with low-pressure oil, in order to ensure balance and carry out the hot oil formed after the hydraulic oil is heated, the hot oil is discharged through the notch and the sector-shaped groove 187.

[0117] Among them, each set of sealing structures can adopt the following structure, including: a pair of sealing retaining rings 20, and the pair of sealing retaining rings 20 are respectively arranged in a pair of sealing retaining ring grooves on the support cover 6 or the rear cover 14. A clamping groove 206 is arranged on the outer periphery of each sealing retaining ring 20 (as shown in Figure 17 ); A sealing ring 19 (as shown in Figure 18) is sleeved on the clamping groove 206 of each sealing retaining ring 20.

[0118] Specifically, each sealing retaining ring adopts a special-shaped sealing retaining ring as shown in Figure 17 . It includes: an inner arc wall 201 formed by a first radius slightly larger than the radius of the optical axis of the tooth shaft 1. The center of the inner arc wall 201 is concentric with the center of the tooth shaft 1 and wraps around the outside of the tooth shaft 1 during assembly; an outer arc wall 204 concentric with the front side plate 8 or the rear side plate 18 and having a radius equivalent to the outer circle radius at the notch on the rear side plate 18. One end of it is fixedly connected to one end of the inner arc wall 201 and forms a sharp-corner-like end with the inner arc wall 201; a connecting wall 203 that fixedly connects the other end of the outer arc wall 204 to the other end of the inner arc wall 201, and it is linear; a first reinforcing rib 202 with one end connected to the junction of the inner arc wall 201 and the connecting wall 203 and the other end connected to the outer arc wall 204; a second reinforcing rib 205 with one end connected to the inner arc wall 201 and the other end connected to the outer arc wall 204, and it is arranged near the sharp-corner-like end. During design, after the sealing retaining ring is assembled on the support cover 6 or the rear cover 14, the oil through holes on the corresponding side plate should be exposed, that is, as shown in Figure 22b , the oil through hole 189 and the oil through hole 184 are located in the space surrounded by the first reinforcing rib 202, the inner arc wall 201, the outer arc wall 204, and the second reinforcing rib 205. The oil through hole 189 is close to the corner where the first reinforcing rib 202 and the inner arc wall 201 are connected. The oil through hole 184 is close to the second reinforcing rib 205. The oil through hole 183 is located in the space surrounded by the first reinforcing rib 202, the connecting wall 203, and the outer arc wall 204 and is close to the connection between the first reinforcing rib 202 and the outer arc wall 204. The sealing retaining ring 20 of this embodiment has sufficient strength and can fully axially seal the side plate and the support cover or the rear cover to prevent axial oil leakage. In addition, a clamping groove 206 is provided in a circular shape on the outer periphery of the sealing retaining ring, and the sealing ring 19 is arranged in the clamping groove 206. The shape of the sealing ring 19 is adapted to the shape of the clamping groove.

[0119] Correspondingly, the shape of each sealing retaining ring groove on the support cover or the rear cover is adapted to the shape of the sealing retaining ring. That is, the sealing retaining ring groove is of a special shape, and its groove wall includes: a first groove wall that is concentric with the inner arc wall and has a radius slightly larger than or equal to the radius of the inner arc wall; a second groove wall that is concentric with the outer arc wall and has a radius slightly larger than or equal to the radius of the outer arc wall, one end of which is fixedly connected to one end of the first groove wall and forms a similar sharp corner end with the first groove wall; a connecting groove wall that fixedly connects the other end of the second groove wall to the other end of the first groove wall, and is linear. When arranging a pair of sealing retaining ring grooves on the support cover or the rear cover, a crescent plate positioning pin hole is provided between the connecting groove walls of the pair of sealing retaining ring grooves, and the similar sharp corner end is close to the shaft hole.

[0120] Alternatively, the sealing structure of this embodiment can also adopt, for example, Figures 39-41 the special-shaped sealing structure 20a shown in the figure. It integrates the functions of the above-mentioned sealing retaining ring and the sealing ring. Its outer shape is basically the same as that of the above-mentioned special-shaped sealing retaining ring. The difference is that the first reinforcing rib 202 and the second reinforcing rib 205 such as those of the above-mentioned sealing retaining ring are not provided inside the special-shaped sealing structure 20a, and a groove 207 is opened on the inner side of the sealing structure 20a. An annular protrusion 208 perpendicular to the end face and protruding outward (i.e., protruding along the direction parallel to the tooth shaft after assembly) is provided around the outer peripheral edge of one end face of the sealing structure 20a. The sealing structure 20a that integrates the functions of the sealing retaining ring and the sealing ring can withstand high temperature and high pressure, is convenient for processing, and is easy to assemble with other accessories. Setting the groove 207 on the sealing structure can increase the axial elasticity of the special-shaped sealing structure, and the outer peripheral annular protrusion 208 is used for the part in contact with the bottom surface of the support cover for sealing. The annular protrusion 208 and one end face of the sealing structure 20a form a structural groove, and the structural groove can hold a certain amount of hydraulic oil, so as to balance the pressure in the inner and outer oil cavities of the corresponding floating side plate. During production, the special-shaped sealing structure is integrally formed by using a tetrafluoro synthetic material that is resistant to high temperature and high pressure.

[0121] In addition to adopting the special-shaped sealing structure 20a with the above structure, the sealing structure of this embodiment can also adopt a sealing structure that integrates the functions of the sealing retaining ring and the sealing ring and has a circular cross-section, such as the cross-sectional shape of an O-ring.

[0122] It should be noted that regardless of the shape of the sealing structure, the shape of the sealing retaining ring groove provided on the front cover or the support cover 6 and the rear cover 14 for arranging the sealing structure is adapted to the external shape of the sealing structure.

[0123] Through the cooperation of the front side plate 8, the rear side plate 18, and the sealing structure, the leakage of hydraulic oil along the axial direction can be effectively prevented, thereby achieving reliable sealing and enabling the fluid machine to work efficiently. By passing the cylindrical portion of a crescent plate positioning pin 13 (i.e., the positioning pin 132) through the front side plate 8 and then inserting it into the crescent plate positioning pin hole 604 of the support cover 6, the wedge-shaped positioning member 131 of the crescent plate positioning pin 13 is inserted into a pair of wedge-shaped grooves 122 on the front end face of the inner crescent plate 12 and the wedge-shaped space formed by a pair of outer crescent plates 11 correspondingly. The cylindrical portion of the other crescent plate positioning pin 13 (i.e., the positioning pin 132) passes through the rear side plate 18 and then is inserted into the crescent plate positioning pin hole 144 of the rear cover 14. The wedge-shaped positioning member 131 of the crescent plate positioning pin 13 is inserted into a pair of wedge-shaped grooves 122 on the rear end face of the inner crescent plate 12 and the wedge-shaped space formed by a pair of outer crescent plates 11 correspondingly. Thus, while circumferentially positioning, preventing detachment, and allowing oil passage of the inner and outer crescent plates through a pair of crescent plate positioning pins 13, axial fixation of the front and rear side plates can also be achieved, achieving multiple benefits, simplifying the structure, facilitating assembly, and ensuring reliable use.

[0124] The gear motor pump of this embodiment can achieve two-way operation, and the radial clearance compensation component and the axial sealing component can effectively prevent internal leakage of hydraulic oil, enabling the fluid machine to have a large displacement and high pressure. Through experimental verification, the flow rate of the fluid machine in this embodiment can reach 160 ml / r, the pressure can reach 35 MPa, and the gear motor pump in this embodiment has excellent heat dissipation performance.

[0125] Embodiment 2

[0126] As Figure 37 shown, it is a schematic structural diagram of the two-way gear motor pump of this embodiment. Different from Embodiment 1, the fluid machine of this embodiment uses a control rear cover with a control function, that is, a pair of overflow valves and a pair of one-way valves are provided on the control rear cover of this embodiment, enabling the fluid machine of this embodiment to be applied to a closed hydraulic system.

[0127] Specifically, as Figures 23-25As shown in the figure, the control rear cover of this embodiment includes a circular rear cover body and a first overflow valve 1420, a second overflow valve 1419, a first one-way valve 1421, and a second one-way valve 1418 mounted on the rear cover body. The overflow valve and the one-way valve both adopt the cartridge-type overflow valve and the cartridge-type one-way valve in the prior art. Among them, the first overflow valve 1420 can adopt a pilot-operated overflow valve, the first one-way valve 1421 can adopt a PCT11-A0 hydraulic control one-way valve, and the second one-way valve 1418 can adopt a CV10-20 one-way valve. In this embodiment, a shaft hole 142, a crescent plate locating pin hole 144, a sealing ring groove 145, a sealing ring groove 143, four screw holes 147, and a locating pin hole 146 are provided on the front end face of the rear cover body facing the pump body 10. The shapes, sizes, and positions of the above-mentioned holes or grooves are the same as those of the corresponding holes or grooves in Embodiment 1, and will not be repeated here.

[0128] Different from Embodiment 1, in this embodiment, oil through holes 1410 and 149 are symmetrically provided on the front end face of the rear cover body. These two oil through holes are blind holes and are respectively paired and communicated with two oil through holes 102 and 106 on the pump body 10, and can be connected to the corresponding oil ports serving as the oil inlet and oil outlet according to the rotation direction of the gear shaft 1. It should be noted that during the assembly of this embodiment, the sealing materials used to block the two oil through holes 102 and 106 on the pump body 10 in Embodiment 1 are removed so that the oil through holes can pass oil.

[0129] A first one-way valve communication hole 1412 (i.e., the hole 1425 on the rear end face of the rear cover body as shown in Figure 30 the figure) and a first overflow valve communication hole 1411 (i.e., the hole 1427 on the rear end face of the rear cover body as shown in Figure 30 the figure) are provided in the sealing ring groove 145. A second one-way valve communication hole 1413 (i.e., the hole 1426 on the rear end face of the rear cover body as shown in Figure 30 the figure) and a second overflow valve communication hole 1414 (i.e., the hole 1425 on the rear end face of the rear cover body as shown in Figure 30The holes 1428) on the rear end face of the rear cover body as shown. On the rear end face of the rear cover body, there are first check valve mounting holes 1425 and first overflow valve mounting holes 1427 corresponding to the positions of the first check valve communication hole 1412 and the first overflow valve communication hole 1411 respectively, and second check valve mounting holes 1426 and second overflow valve mounting holes 1428 corresponding to the positions of the second check valve communication hole 1413 and the second overflow valve communication hole 1414 respectively. The first check valve 1421 and the first overflow valve 1420 are respectively installed in the first check valve mounting hole 1425 and the first overflow valve mounting hole 1427, and the second check valve 1418 and the second overflow valve 1419 are respectively installed in the second check valve mounting hole 1426 and the second overflow valve mounting hole 1428. The oil path between the first check valve communication hole 1412 and the first check valve mounting hole 1425 is opened or closed by the first check valve 1421, and the oil path between the second check valve communication hole 1413 and the second check valve mounting hole 1426 is opened or closed by the second check valve 1418.

[0130] The first check valve 1421 and the first overflow valve 1420 are taken as a group, and the second check valve 1418 and the second overflow valve 1419 are taken as another group. The two groups of valves can provide corresponding support for the forward and reverse rotation of the fluid machine. For example, a pair of overflow valves can provide overpressure protection for the hydraulic oil pressure in the pump body during forward or reverse rotation, and when there is oil in the system, a pair of check valves open the corresponding oil paths to drain or inlet oil.

[0131] In addition, a plurality of process holes 148, 1415, 1416, 1422, 1423, 1424, 1417 are provided on the outer periphery of the rear cover body for facilitating the machining of each hole passage on the rear cover body and for external oil leakage or external connection of joints. Each process hole can be blocked or not blocked according to needs. When not blocked, corresponding joints can be connected according to needs. For example, when measuring the back pressure, a pressure measuring joint can be connected at the corresponding process hole. Each hole can be machined into a through hole, a counterbore or a threaded hole according to needs.

[0132] As Figure 31 shown, the oil passage hole 1410 of this embodiment is communicated with the first overflow valve communication hole 1411, the shaft hole 142 is communicated with the process hole 148, the second overflow valve communication hole 1414 is communicated with the oil passage hole 149, the oil passage hole 149 is communicated with the process hole 1424, and the process hole 1424 is communicated with the process hole 1416. As Figure 32 shown, the process hole 1415 is communicated with the first overflow valve communication hole 1411 (i.e., hole 1427), and the process hole 1423 is communicated with the second overflow valve communication hole 1414 (i.e., hole 1428). As Figure 33 shown, the second check valve communication hole 1413 (i.e., hole 1426) is communicated with the process hole 1423. AsFigure 34 As shown, the first one-way valve communication hole 1412 (i.e., hole 1425) is communicated with the process hole 1417, the process hole 1417 is communicated with the second one-way valve communication hole 1413 (i.e., hole 1426), and the second one-way valve communication hole 1413 (i.e., hole 1426) is communicated with the process hole 1423. As Figure 35 As shown, the shaft hole 142 is communicated with the process hole 1416 and the process hole 148. The process hole 1417 can be communicated with the shaft hole 142.

[0133] The process hole 1424 serves as the oil drain hole of the second one-way valve. It is not communicated with the joint. It is a process hole used to open 149, 148, and 146 and can be sealed. The process hole 1417 serves as the oil drain hole during external oil leakage and the pressure measurement hole when measuring the back pressure after connecting the pressure measurement joint. 1416 is the oil drain hole when the first one-way valve drains oil. Each overflow valve and one-way valve are connected to the rear cover body by the threaded two-way cartridge method. The corresponding process holes that are communicated with the installation holes of each valve and are located in the circumferential direction of the rear cover body are the oil outlets, and the hole openings facing the pump body end are the oil inlets.

[0134] It should be noted that when adopting this embodiment, the oil inlet of the external oil leakage hole provided on the rear cover needs to be communicated with the oil inlet port of the pilot overflow valve.

[0135] Except for the above-mentioned rear cover, the front cover, pump body and other components of the bidirectional gear motor pump in this embodiment are the same as those in Embodiment 1, and the structures of each component will not be described in detail here.

[0136] Embodiment 3

[0137] The bidirectional gear motor pump in this embodiment can adopt the structure of Embodiment 1, and on the basis of Embodiment 1, heat dissipation grooves for heat dissipation are provided on the rear end face of the rear cover 14, as Figure 38 shown, the heat dissipation grooves include a plurality of longitudinal grooves and a plurality of transverse grooves, and the plurality of longitudinal grooves and the plurality of transverse grooves intersect with each other.

[0138] Although the present invention has been described in detail above, the present invention is not limited thereto. Those skilled in the art of this technology can make modifications according to the principle of the present invention. Therefore, all modifications made according to the principle of the present invention should be understood to fall within the protection scope of the present invention.

Claims

1. A two-way gear motor pump, comprising a tooth shaft, a front cover, a pump body, a rear cover, an internal gear ring, an axial seal assembly having a pair of side plates, a radial clearance compensation assembly, and an external oil leakage channel for circulating the hydraulic oil that gets heated inside the pump body towards the outside of the pump body, wherein: The external oil leakage channel includes: a first channel formed by the gap between the front side plate of the pair of side plates, the front cover, and the tooth shaft; a second channel formed by the gap between the rear side plate of the pair of side plates, the rear cover, and the tooth shaft; a third channel opened on the tooth shaft and having its oil inlet connected to the first channel and its oil outlet connected to the second channel; a fourth channel opened on the rear cover and having its oil inlet connected to the second channel and the third channel respectively, which penetrates the rear cover axially along the rear cover or extends from the center of the rear cover to the outer wall of the rear cover radially along the rear cover; The pump body is hollow to form an inner cavity for arranging the internal gear ring, the radial clearance compensation assembly, and the outer gear part of the tooth shaft therein, located between the front cover and the rear cover; the front cover, the pump body, and the rear cover are connected together by bolts and flat washers, and a pointed angle groove for gradually decompressing and unloading the rotating seal cavity during the operation of the motor pump is provided on the front end face of the rear side plate of the pair of side plates facing the pump body; The radial clearance compensation assembly includes an inner crescent plate extending in a crescent shape from its middle part towards both sides and a pair of outer crescent plates arranged symmetrically outside the inner crescent plate and in a crescent shape. A pair of hook-shaped parts protruding towards the outer crescent plates are provided on the outer wall of the inner crescent plate, and anti-detachment grooves adapted to the shapes of the corresponding hook-shaped parts are provided on the inner walls of each of the pair of outer crescent plates. The hook-shaped parts can be clamped in the anti-detachment grooves; The first channel and the second channel are connected by a pair of arc-shaped grooves provided at the bottoms of the pair of hook-shaped parts of the inner crescent plate and penetrating the front end face and the rear end face of the inner crescent plate to form an oil leakage balance channel.

2. The bi-directional gear motor pump according to claim 1, wherein The third channel includes: A radial oil leakage hole opened in the middle of the tooth shaft and extending radially from its center. The oil inlet of the radial oil leakage hole is opened on the outer wall of the tooth shaft; An axial oil leakage hole opened on the tooth shaft and extending along its axis. Its oil inlet is connected to the oil outlet of the radial oil leakage hole, and its oil outlet is connected to the second channel.

3. The two-way gear motor pump according to claim 1, wherein: Wedge-shaped grooves are respectively opened in the middle parts of the front end face and the rear end face of the inner crescent plate; A wedge-shaped space is formed between the opposite end faces of the pair of outer crescent plates; A pair of wedge-shaped positioning members for positioning and oil passage and pressure relief are respectively arranged in the pair of wedge-shaped grooves and the wedge-shaped space of the inner crescent plate; Wherein, the wedge-shaped positioning members have the same shape as the wedge-shaped grooves but have a gap.

4. The bi-directional gear motor pump according to claim 1, characterized in that, Multiple anti-friction oil grooves for equalizing the pressure on the internal gear ring are provided on the inner hole wall of the pump body.

5. The bi-directional gear motor pump according to claim 3, characterized in that, The axial seal assembly further includes a pair of positioning pins installed at both ends of the pump body and passing through the pair of side plates and the front cover and the rear cover respectively, and the positioning pins are fixedly connected or integrally formed with the corresponding wedge-shaped positioning members as crescent plate positioning pins.

6. The bi-directional gear motor pump according to any one of claims 1-5, characterized in that, The front end face of the rear cover is provided with a shaft hole for arranging the rear end of the tooth shaft, and the shaft hole is connected to the fourth channel.

7. The bi-directional gear motor pump according to claim 1, characterized in that, The rear cover is a control rear cover with control functions or an ordinary rear cover without control functions. A pair of overflow valve jacks and a pair of one-way valve jacks are provided on the control rear cover. A pair of oil through holes that are symmetric about the center of the rear cover are formed on the rear end face of the pump body for connecting with the rear cover.

8. The bi-directional gear motor pump according to claim 7, characterized in that, A heat dissipation groove for heat dissipation is provided on the rear end face of the rear cover.

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