WO2020253471A1

WO2020253471A1 - Reciprocating sealing-ring-free piston hydraulic braking device

Info

Publication number: WO2020253471A1
Application number: PCT/CN2020/092087
Authority: WO
Inventors: 刘蕴星
Original assignee: 刘蕴星
Priority date: 2019-06-21
Filing date: 2020-05-25
Publication date: 2020-12-24
Also published as: CN110145559A; CN110500369A

Abstract

Disclosed is a reciprocating sealing-ring-free piston hydraulic braking device comprising: a hydraulic cylinder provided with a cylinder cover (20), a cylinder body (9002), and a sealing-ring-free piston (19) capable of reciprocal movement in the cylinder body; a clutch mechanism provided with a clutch housing (3) and a crankshaft machine body (9) which are connected to each other; and a clutch semi-axle (4) arranged in the clutch housing, a clutch spline sleeve (5) arranged outside the clutch semi-axle, a crankshaft (8) arranged in the crankshaft machine body, and a transmission gear (1) connected to the clutch semi-axle; and a transmission mechanism, wherein the transmission mechanism drives the sealing-ring-free piston to move, and force generated during compression and pump suction of the sealing-ring-free piston forms restoring torque to be transmitted to the crankshaft, and transmitted to a main shaft of a power device by means of the clutch mechanism. The hydraulic braking device has the advantages that the structure is simple, manufacturing is convenient, mounting is flexible, little liquid working media is used, the braking efficiency is high, and the reliability is good.

Description

Reciprocating piston hydraulic brake device without seal ring

Technical field

The invention relates to the field of mechanical engineering, in particular, to a reciprocating piston hydraulic brake device without a seal ring.

Background technique

Common hydraulic retarder is composed of rotor, stator, working chamber, input shaft, heat exchanger, oil storage tank and shell. The stator and the rotor oppose each other to form a working chamber, which communicates with a working fluid storage tank (oil pool) through a valve. When slowing down, the electronic control system controls the proportional valve to apply air pressure to the working fluid storage tank to fill the working chamber with the working fluid, and the rotor generates a retarding torque to slow the car. While the rotor is rotating in the working fluid, the working fluid circulates through the heat exchanger under the action of the pressure difference between the inlet and outlet formed by the movement. The cooling water pipe leading to the engine cooling system from the heat exchanger takes the heat to the engine cooling system for dissipation. Drop. When the retarding effect is released, the control device system releases the working fluid back to the working fluid storage tank, thereby eliminating the resistance to the rotor.

Although the existing technical solutions can achieve a good braking effect, the disadvantages are complex structure, high cost, long response time (usually within 1-2 seconds) and power loss during operation.

Summary of the invention

technical problem

In view of this, the purpose of the present invention is to provide a reciprocating seal-ring-free piston hydraulic brake device with simple structure, convenient manufacture, flexible installation, less use of liquid working media, high braking efficiency and good reliability.

The solution to the problem

Technical solutions

To this end, the present invention provides a reciprocating seal-ring-free piston hydraulic brake device, including: a hydraulic cylinder including: a cylinder head, a cylinder block, a seal-ring-free piston capable of reciprocating in the cylinder; a clutch mechanism , Comprising: a clutch housing and a crankshaft body connected to each other; a clutch half shaft provided in the clutch housing and a clutch spline sleeve provided outside the clutch half shaft; a crankshaft provided in the crankshaft body, And the transmission gear connected with the clutch half shaft; when the clutch mechanism is disengaged, the keys in the clutch spline sleeve cooperate with the teeth of the crankshaft, and when the clutch mechanism is working, the clutch spline sleeve The key in the barrel meshes with the teeth of the clutch half shaft and the teeth of the crankshaft at the same time; the transmission mechanism drives the movement of the piston without seal ring.

The invention mainly consists of a piston hydraulic cylinder without a seal ring, a clutch mechanism and a transmission mechanism. The force generated by the compression and pumping of the reciprocating piston in the hydraulic cylinder forms a reaction torque and is transmitted to the crankshaft, and is transmitted to the main shaft of the power unit that needs to be decelerated through the clutch mechanism to realize the deceleration and braking function of the power unit. At the same time, due to the adoption of the clutch mechanism, the response time can be shortened and the power loss is basically zero.

Preferably, the transmission mechanism includes: a crankshaft connecting rod connecting plate connected with the crankshaft, a connecting rod pin connected with the crankshaft connecting rod connecting plate, a connecting rod connected with the connecting rod pin, and A piston pin connected by a connecting rod, the piston pin is connected with the piston without a seal ring to drive its movement.

Preferably, the transmission mechanism has: a main connecting rod structure and an auxiliary connecting rod, the main connecting rod structure is divided into a connecting rod small end, a connecting rod, and a connecting rod large end; the connecting rod small end is provided with a piston pin hole The connecting rod head is provided with an auxiliary connecting rod connecting hole for inserting the auxiliary connecting rod; the connecting rod pin penetrates the auxiliary connecting rod connecting hole of the connecting rod head and the auxiliary connecting rod is connected with the main connecting rod; The other end of the connecting rod is connected with the non-seal ring piston through a piston pin.

Preferably, the clutch mechanism further includes a clutch half shaft thrust plate that restricts the movement of the clutch half shaft and a crankshaft axial thrust plate that restricts the axial movement of the crankshaft.

Preferably, the clutch mechanism further includes a clutch fork assembly that pushes the clutch spline sleeve to move toward the clutch half shaft.

On the other hand, the present invention also provides a reciprocating seal-ring-free piston hydraulic brake device, including: a hydraulic cylinder including: a cylinder head, a cylinder block, and a seal-ring-free piston capable of reciprocating within the cylinder; A clutch mechanism includes: a clutch housing and a crankshaft body connected to each other, the crankshaft body is provided with a crankshaft; the force generated by the compression and pumping of the seal-less piston is transmitted to the crankshaft through the reaction torque The clutch mechanism is transmitted to the main shaft of the power unit; the transmission mechanism, which drives the piston without seal ring, includes: a crankshaft connecting rod connecting plate connected to the crankshaft, a connecting rod pin connected to the crankshaft connecting rod connecting plate, A connecting rod connected with the connecting rod pin, a piston pin connected with the connecting rod, and the piston pin connected with the piston without a seal ring to drive its movement.

In addition, the present invention also provides a reciprocating seal-ring-free piston hydraulic brake device, including: a hydraulic cylinder, including: a cylinder head, a cylinder block, a seal-free piston capable of reciprocating in the cylinder; a clutch mechanism , Provided with: a clutch housing and a crankshaft body connected to each other, the crankshaft is provided in the crankshaft body; the force generated during compression and pumping of the seal-free piston forms a reaction torque and is transmitted to the crankshaft through the clutch mechanism Is transmitted to the main shaft of the power unit; a transmission mechanism, which drives the movement of the piston without a seal ring, is provided with: a main connecting rod and an auxiliary connecting rod. The main connecting rod is divided into a connecting rod small end, a connecting rod, and a connecting rod large end; The small end of the connecting rod is provided with a piston pin hole, and the large end of the connecting rod is provided with an auxiliary connecting rod connecting hole for inserting the auxiliary connecting rod; the connecting rod pin penetrates the auxiliary connecting rod connecting hole and the auxiliary connecting rod of the connecting rod large end Connected with the main connecting rod; the small end of the connecting rod and the other end of the auxiliary connecting rod are connected with the non-seal ring piston through a piston pin.

Preferably, it further comprises a crankshaft body cover plate connected with the crankshaft body to form a closed cavity inside the crankshaft body.

Preferably, it also includes a cooling water channel independent of the internal cavity of the crankshaft body.

Preferably, a throttle valve oil inlet pipe, a throttle valve component and a throttle valve oil return pipe are connected between the cylinder head and the internal cavity of the crankshaft body.

Preferably, the side wall of the piston without a seal ring is provided with a high-pressure groove for a liquid working meson.

Preferably, the clutch spline sleeve has splines inside, and the tooth profile angle of the end of the clutch spline sleeve is 0-30 degrees.

Preferably, there is a gap between the side wall of the piston without a seal ring and the cylinder.

Preferably, it further includes a liquid working meson storage box component, the liquid working meson storage box component includes a three-way pipe, an air pressure balance pipe, a liquid working meson storage tank body, and a pressure-air regulating proportional valve, the three-way pipe Located at the bottom of the crankshaft body cover plate and the liquid working meson storage tank, which is lower than the air pressure balance pipe in the vertical direction; the air pressure balancing pipe is connected to the throttle valve return pipe and the liquid working meson storage tank The part connected with the throttle valve return pipe is close to the throttle valve body; the connecting part of the air pressure balance pipe and the liquid working meson storage tank body is located in the non-working state of the liquid working meson storage tank inside the liquid working meson Above the liquid level.

Preferably, the cylinder head is provided with a one-way valve, and the one-way valve of each cylinder head of the plurality of hydraulic cylinders is connected with the throttle valve oil inlet pipe after being connected by a common rail oil pipe, forming a multi-cylinder connected inlet The structure of tubing common rail.

Preferably, the cylinder head is provided with a one-way valve, the one-way valve includes a one-way valve spool with a stepped outer diameter, and a one-way valve pressure is provided at a small outer diameter portion of the one-way valve spool The balance hole penetrates the small diameter part of the outer circle and the inner hole of the valve core.

Preferably, an annular groove distributed in a circumferential direction is formed on the side wall of the piston without a seal ring.

The beneficial effects of the invention

Brief description of the drawings

Description of the drawings

1 is a schematic diagram of the appearance of a reciprocating piston hydraulic brake device without a seal ring according to an embodiment of the present invention, wherein (a) is a right view, (b) is a front view, and (c) is a left view.

Fig. 2 is an A-A' view of the device shown in Fig. 1(a), showing the structure of a reciprocating piston hydraulic brake device without a seal ring according to an embodiment of the present invention.

Fig. 3 is a schematic structural diagram of the clutch mechanism in the device shown in Fig. 2.

Fig. 4 is a schematic structural diagram of a piston hydraulic cylinder without a seal ring in the device shown in Fig. 2.

Fig. 5 is a B-B' view of the device shown in Fig. 1(b), showing the structure of the transmission mechanism in the device shown in Fig. 2.

Fig. 6 is a schematic diagram of the structure of the hydraulic cylinder head in the device shown in Fig. 2.

Fig. 7 is a schematic structural diagram of a throttle mechanism in the device shown in Fig. 2.

Fig. 8 is a structural schematic diagram of the clutch fork assembly in the device shown in Fig. 2.

Fig. 9 is a schematic structural diagram of a reciprocating piston hydraulic brake device without a seal ring according to another embodiment of the present invention.

Fig. 10 is a structural schematic diagram of the liquid working meson storage box part of the device shown in Fig. 9.

Fig. 11 is a schematic diagram of the structure of the clutch spline sleeve in the device shown in Fig. 2, in which (a) is a front view, and (b) is a left view.

Fig. 12 is a schematic structural diagram of the crankshaft connecting rod connecting plate in the device shown in Fig. 2, wherein (a) is a front view, and (b) is a side view.

Fig. 13 is a schematic structural diagram of the crankshaft axial thrust plate in the device shown in Fig. 2, wherein (a) is a side view, and (b) is a front view.

Fig. 14 is a schematic structural view of Embodiment 1 of the piston without a seal ring in the device shown in Fig. 2, in which (a) is a front sectional view, (b) is a left view, and (c) is a top view.

Fig. 15 is a schematic structural diagram of Embodiment 2 of the piston without a seal ring in the device shown in Fig. 2, wherein (a) is a front sectional view, (b) is a left side view, and (c) is a top view.

16 is a schematic structural view of Embodiment 3 of the piston without a seal ring in the device shown in FIG. 2, wherein (a) is a front sectional view, (b) is a left view, and (c) is a top view.

Fig. 17 is a schematic structural view of Embodiment 4 of the piston without a seal ring in the device shown in Fig. 2, wherein (a) is a front sectional view, (b) is a left view, and (c) is a top view.

18 is a schematic structural view of Embodiment 5 of the piston without a seal ring in the device shown in FIG. 2, wherein (a) is a front sectional view, (b) is a left view, and (c) is a top view.

Fig. 19 is a schematic diagram of the horizontally symmetrical arrangement of the seal-less piston connecting rod mechanism in the device shown in Fig. 2.

Figure 20 is a schematic diagram of the main and auxiliary connecting rods.

Figure 21 is a schematic diagram of the common rail structure of the throttle valve inlet pipe.

Reference signs: 1 transmission gear; 2 clutch spline half shaft thrust plate; 3 clutch housing; 4 clutch spline half shaft; 5 clutch spline sleeve; 6 clutch fork assembly; 7 crankshaft axial thrust plate ; 8 crankshaft; 9 crankshaft body; 10 crimping nut live joint; 11 crankshaft body cover; 12 connecting rod journal; 13 crankshaft connecting rod connecting plate stopper; 14 crankshaft connecting rod connecting plate; 15 connecting rod pin; 16 Connecting rod; 17 throttle valve parts; 18 piston pin; 19 piston without sealing ring; 20 hydraulic cylinder head parts; 21 pressure plate; 22 bolts; 23 liquid working meson storage box parts; 24 main connecting rod; 25 common rail oil pipe; 6001 shift fork; 6002 fixed pin; 6003 slide rail; 9001 cooling water channel; 9002 hydraulic cylinder block; 1701 throttle valve return pipe; 1702 throttle valve body; 1703 throttle valve disc; 1704 throttle valve inlet pipe; 2001 one-way valve sealing bolt; 2002 one-way valve compression spring; 2003 one-way valve pressure balance hole; 2004 one-way valve spool; 2005 hydraulic cylinder head; 2301 three-way pipe; 2302 air pressure balance pipe; 2303 liquid working meson Storage tank body; 2304 pressure air regulating proportional valve; 2401 pair of connecting rods.

The best embodiment for implementing the invention

The best mode of the invention

The present invention will be further described below in conjunction with the drawings and the following embodiments. It should be understood that the drawings and the following embodiments are only used to illustrate the present invention, not to limit the present invention.

Figure 1 is a schematic diagram of the appearance of a reciprocating piston hydraulic brake device without a seal ring according to an embodiment of the present invention, in which (a) is a right view, (b) is a front view, and (c) is a left view; 2 is the AA' view of the device shown in Fig. 1(a), showing the structure of a reciprocating piston hydraulic brake device without a seal ring according to an embodiment of the present invention. As shown in FIG. 1 and FIG. 2, the reciprocating type non-seal-ring piston hydraulic brake device of this embodiment includes a clutch mechanism, a non-seal-ring piston hydraulic cylinder, and a transmission mechanism.

The device of the present invention uses the force generated during compression and pumping of the reciprocating piston in the hydraulic cylinder to form a reaction torque that is transmitted to the crankshaft, and is transmitted to the main shaft of the power device that needs to be decelerated through the clutch mechanism to realize the deceleration and braking function of the power device. At the same time, due to the adoption of the clutch mechanism, the response time can be shortened and the power loss is basically zero.

Specifically, the crankshaft drives the piston in the hydraulic cylinder to reciprocate via the crankshaft connecting rod connecting plate. The crankshaft connecting rod connecting plate structure has the characteristics of simple processing and manufacturing technology, convenient installation with connecting rod pins and connecting rods, and a small number of parts, which makes the cost lower. In addition to the crankshaft connecting rod connecting disc structure, the main and auxiliary connecting rod structure shown in FIG. 20 can also be used to achieve the same function and performance. The main connecting rod is divided into three parts: connecting rod small end, connecting rod and connecting rod big end. The small end of the connecting rod has a piston pin hole, and the large end of the connecting rod can add a secondary connecting rod connection hole in the circumferential direction according to the layout needs. The connecting hole for the auxiliary connecting rod of the big end of the connecting rod is a groove design for inserting the auxiliary connecting rod. One end of the auxiliary connecting rod is provided with a connecting rod pin hole, and the other end is provided with a piston pin hole. The connecting rod pin penetrates the auxiliary connecting rod connecting hole of the big end of the connecting rod and the connecting rod pin hole of the auxiliary connecting rod, so that the auxiliary connecting rod is connected with the main connecting rod. The small end of the connecting rod and the other end of the auxiliary connecting rod are connected to the piston without a seal ring by inserting a piston pin into the respective piston pin hole.

Fig. 3 is a schematic structural diagram of the clutch mechanism in the device shown in Fig. 2. As shown in Figures 2 and 3, the transmission gear 1, the clutch spline half shaft thrust plate 2, the clutch housing 3 and the clutch spline half shaft 4 form half of the clutch. The clutch spline sleeve 5, the clutch dial The fork assembly 6, the crankshaft axial thrust plate 7, the crankshaft 8 and the crankshaft body 9 constitute the other half of the clutch. The flange surface of the clutch housing 3 and the flange surface of the crankshaft body 9 are connected by bolts to form a clutch mechanism. In the disengaged state of the clutch mechanism, the clutch spline sleeve 5 is in clearance fit with the spline of the crankshaft 8 through the internal splines. During operation, the movement of the clutch spline sleeve 5 realizes that the splines in the clutch spline sleeve 5 mesh with the splines of the clutch spline half shaft 4 and the splines of the crankshaft 8 at the same time to realize the torque transmission function.

Fig. 11 is a schematic structural diagram of the clutch spline sleeve in the device shown in Fig. 2. As shown in Fig. 11(b), the clutch spline sleeve 5 has splines inside. As shown in Figure 11(a), the 0-30 degree chamfer structure from the root of the spline to the top of the tooth and the end face of the spline sleeve can reduce the internal spline and clutch spline half of the clutch spline sleeve 5. The impact force between the tooth top and the tooth top when the spline of the shaft 4 meshes, avoids damage to the tooth top due to the impact force, and improves the reliability and service life of the parts.

As shown in FIG. 2, the transmission gear 1 is connected to the end of the clutch spline half shaft 4 away from the crankshaft 8. The clutch spline half shaft 4 is formed to include a large-diameter portion and a small-diameter portion, and a flange portion that protrudes radially at the junction of the large-diameter portion. The clutch spline sleeve 5 is arranged outside the small diameter part and the flange part, and one end has an annular groove that is matched with the shift fork.

The clutch spline half shaft thrust plate 2 has a ring shape. The end face of the pressure plate 21, the transmission gear end face and the clutch spline half shaft thrust plate end face are axially pressed by bolts 22 to form a flange portion and the other flange portion Work together to realize the clutch spline half shaft thrust.

Fig. 13 is a schematic structural diagram of the crankshaft axial thrust plate in the device shown in Fig. 2, wherein (a) is a side view, and (b) is a front view. As shown in Fig. 13, the crankshaft axial thrust plate 7 has a ring shape with a bolt hole structure in the circumferential direction. The bolts are connected with the end face of the crankshaft to form a flange that cooperates with the flange on the other side of the crankshaft to realize the axial thrust of the crankshaft.

Fig. 8 is a structural schematic diagram of the clutch fork assembly in the device shown in Fig. 2. As shown in Figure 8, the clutch fork assembly 6 is composed of a fork 6001; a fixed pin 6002; and a sliding rail 6003. The shift fork is connected with the sliding rail by a fixed pin, and the shift fork is matched with the groove of the clutch spline sleeve. The shift fork assembly is driven by the axial movement of the slide rail, and the shift fork drives the movement of the clutch spline sleeve.

As shown in Figure 2, the crankshaft axial thrust plate 7 and the crankshaft 8 are axially installed and connected by bolts to form a boss on one side of the crankshaft main journal, and a boss on the other side of the crankshaft main journal to realize the crankshaft main journal and The installation and coordination of the crankshaft body can limit the axial movement of the crankshaft. The connecting rod journal 12 of the crankshaft 8, the crankshaft connecting rod connecting plate 14, the connecting rod pin 15, the connecting rod 16, the piston pin 18 and the piston without a seal ring 19 are connected together, and the piston 19 without a seal ring is driven by the circular movement of the crankshaft 8. The reciprocating movement is performed in the cylinder block 9002 of the hydraulic cylinder.

Fig. 4 is a schematic structural diagram of a piston hydraulic cylinder without a seal ring in the device shown in Fig. 2. As shown in Figures 2 and 4, the seal-less piston 19, the hydraulic cylinder block 9002, and the hydraulic cylinder head member 20 form a closed working chamber. The crankshaft body cover plate 11 is connected with the crankshaft body 9 through bolts to form a closed internal cavity of the crankshaft body for accommodating the liquid working meson.

Furthermore, the above-mentioned two chambers (that is, the working chamber and the internal cavity of the crankshaft body) are separated by a piston, and the working chamber is operated by the compression and pumping action of the piston. The internal cavity of the crankshaft body is used to store the hydraulic working meson. At the same time, it can also be connected with the hydraulic working meson storage tank (as in the second embodiment described later) to realize the pressurization of the working meson and increase the output of the braking torque.

Fig. 5 is a B-B' view of the device shown in Fig. 1(b), showing the structure of the transmission mechanism in the device shown in Fig. 2. As shown in Figures 2 and 5, the connecting rod journal 12 of the crankshaft 8, the crankshaft connecting rod connecting plate 14, the connecting rod pin 15, the connecting rod 16, the piston pin 18 and the sealless piston 19 are connected together to form a transmission mechanism. The circular movement of the crankshaft 8 drives the piston 19 to reciprocate in the hydraulic cylinder 9002. In this embodiment, only one hydraulic cylinder is shown, and FIG. 5 also only shows that the crankshaft 8 drives the pistons in one hydraulic cylinder to reciprocate through the crankshaft connecting rod connecting plate 14. However, the present invention is not limited to this, and multiple hydraulic cylinders may also be provided. When multiple hydraulic cylinders are provided, the crankshaft connecting rod connecting plate 14 can connect multiple connecting rods. In this way, the crankshaft 8 can drive the pistons in the multiple hydraulic cylinders to reciprocate through the crankshaft connecting rod connecting disc 14 to realize the multiplication of the braking effect.

Fig. 12 is a schematic structural diagram of the crankshaft connecting rod connecting plate in the device shown in Fig. 2, wherein (a) is a front view, and (b) is a side view. As shown in Figure 2 and Figure 12, the side of the crankshaft connecting rod connecting plate is provided with a groove for inserting the connecting rod. The crankshaft connecting rod connecting plate also has a plurality of through holes distributed in the circumferential direction, and the connecting rod pin penetrates the through holes and the connecting rod to connect the crankshaft connecting rod connecting plate and the connecting rod. The other end of the connecting rod is connected with a piston without a seal ring through a piston pin. The crankshaft connecting rod connecting disc baffle 13 has a central hole disc-shaped structure, which is pressed and fixed on the crankshaft by bolt end faces to prevent the crankshaft connecting rod connecting disc from axial movement.

Fig. 6 is a schematic diagram of the structure of the hydraulic cylinder head in the device shown in Fig. 2. As shown in FIG. 6, the hydraulic cylinder head member 20 includes a check valve and a hydraulic cylinder head 2005. The one-way valve is equipped with one-way valve sealing bolt 2001; one-way valve compression spring 2002; one-way valve pressure balance hole 2003; one-way valve spool 2004. The check valve core 2004 adopts a tapered surface seal and an outer diameter stepped design. The part connected with the tapered surface is a small diameter, and the matching part with the cylinder head inner hole is a large diameter. The large and small diameters form an external circular step. The pressure balance hole 2003 of the one-way valve is located at the small diameter part of the outer circle. It penetrates the small diameter of the outer circle and the inner hole of the valve core to achieve internal and external pressure balance. The one-way valve sealing bolt is tightened with the inner hole of the one-way valve of the hydraulic cylinder head. One end of the one-way valve compression spring is clearance fit with the boss of the one-way valve sealing bolt through the inner diameter, and the other end is matched with the check valve spool through the outer diameter. The inner hole clearance fit of the check valve spring pushes the conical surface of the check valve core to match the conical surface of the check valve inner hole of the hydraulic cylinder head to form a conical surface seal.

Fig. 7 is a schematic structural diagram of a throttle mechanism in the device shown in Fig. 2. As shown in Figure 7, the throttle valve mechanism includes: a throttle valve body 1702; a throttle valve plate 1703 arranged in the throttle valve body; and a throttle connected to the internal cavity of the crankshaft body and the throttle valve body. Valve oil return pipe 1701; Throttle valve oil inlet pipe 1704 connected with the working chamber and the throttle body. By controlling the opening of the throttle valve member 17 (throttle valve disc 1703), the pressure in the compression working chamber is increased. The pressure acts on the top surface of the piston 19 without a seal ring to generate pressure, and the pressure passes through the piston pin 18 and the connecting rod 16. , The connecting rod pin 15, the crankshaft connecting rod connecting plate 14, the radial force is converted into an axial torque opposite to the operating direction of the crankshaft 8. The torque passes through the crankshaft 8, the clutch spline sleeve 5, the clutch spline half shaft 4 and The transmission gear 1 is transmitted to the external transmission mechanism, thereby realizing deceleration and braking of the external transmission mechanism.

The working principle of the reciprocating seal-ring-less piston hydraulic brake device of this embodiment: through the reciprocating movement of the seal-less piston 19, the compression force and negative pressure generated in the hydraulic cylinder act on the piston connecting rod mechanism to produce The reverse torque of the crankshaft runs opposite, and the torque is transmitted to the external transmission mechanism through the clutch mechanism to realize the deceleration and braking of the external transmission mechanism.

The working process of the reciprocating sealing ring-less piston hydraulic brake device of this embodiment: when the external transmission mechanism drives the transmission gear 1 to rotate, the transmission gear 1 drives the clutch spline shaft 4 to rotate, and the clutch fork assembly 6 pushes the clutch spline The sleeve 5 moves in the direction of the clutch spline half shaft 4 and engages with the splines on the clutch spline half shaft 4 to connect the clutch spline half shaft 4 with the crankshaft 8 to drive the crankshaft 8 to rotate. During the rotation of the crankshaft 8, the crankshaft connecting rod connecting disc 14 is driven to perform circular movement. When the crankshaft connecting rod connecting disc 14 drives the connecting rod 16 to make circular motions through the connecting rod pin 15, the connecting rod 16 drives the non-seal piston 19 through the piston pin 18 The hydraulic cylinder 9002 makes a reciprocating linear movement. When the seal-less piston 19 moves toward the hydraulic cylinder head part 20, it compresses the liquid working meson in the working chamber. The liquid working meson passes through the one-way valve of the hydraulic cylinder head part 20 and enters the throttle valve from the oil outlet. The oil pipe 1704 reaches the throttle valve plate 1703, and finally returns to the internal cavity of the crankshaft body through the throttle valve oil return pipe 1701.

When the external transmission mechanism drives the transmission gear 1 to rotate, the transmission gear 1 drives the clutch spline half shaft 4 to rotate, and the clutch fork assembly 6 pushes the clutch spline sleeve 5 to move in the direction of the clutch spline half shaft 4, and the clutch spline half shaft The splines on 4 are engaged, and the clutch spline half shaft 4 is connected with the crankshaft 8 to drive the crankshaft 8 to rotate. During the rotation of the crankshaft 8, the crankshaft connecting rod connecting disc 14 is driven to perform circular movement. When the crankshaft connecting rod connecting disc 14 drives the connecting rod 16 to make circular motions through the connecting rod pin 15, the connecting rod 16 drives the non-seal piston 19 through the piston pin 18 The hydraulic cylinder 9002 makes a reciprocating linear movement. When the seal-less piston 19 moves in the opposite direction of the hydraulic cylinder head part 20, a vacuum is formed in the working chamber, and negative pressure is generated. This pressure is equal to the pressure generated by the fluid pressure in the internal cavity of the body acting on the back of the seal-less piston 19 , The pressure through the piston pin 18, the connecting rod 16, the connecting rod pin 15, the crankshaft connecting rod connecting plate 14, the radial force is converted into an axial torque opposite to the crankshaft 8 operating direction, this torque passes through the crankshaft 8, the clutch spline sleeve The cylinder 5, the clutch spline shaft 4 and the transmission gear 1 are transmitted to the external transmission mechanism, thereby realizing the deceleration and braking of the external transmission mechanism.

Through the combined force of the above two forces, the generated reverse axial moment effect jointly realizes the deceleration and braking effect on the external transmission mechanism. At the same time, as the number of hydraulic cylinders increases, piston area increases, and piston stroke increases, the braking effect will be further enhanced.

During the working process, the liquid working medium is compressed and absorbs the energy of the external transmission mechanism to generate a temperature rise. Therefore, it also includes a cooling water channel 9001 independent of the internal cavity of the crankshaft body. The cooling water passes through the cooling water channel 9001 to cool the liquid working medium. The cooling water channel of the body can be directly connected to an external cooling water device to take away the heat generated during the working process.

Fig. 9 is a schematic structural diagram of a reciprocating piston hydraulic brake device without a seal ring according to another embodiment of the present invention. In this embodiment, a liquid working meson storage box component 23 is added. By increasing the pressure of the working meson storage tank, it pressurizes the liquid working meson in the internal cavity of the crankshaft body to increase the output of pressure and negative pressure, and at the same time increase the output of reverse torque, increase the output of braking torque, and improve the braking effect .

The liquid working meson storage tank component 23 is composed of a three-way pipe 2301, an air pressure balance pipe 2302, a liquid working meson storage tank body 2303, and a pressure air regulating proportional valve 2304. One end of the three-way pipe 2301 is connected to the crankshaft body cover 11 through a crimping nut 10, the other end is connected to the throttle valve return pipe 1701, and the liquid working meson storage tank 2303 is connected at the same time. The three-way pipe 2301 is located at the bottom of the crankshaft body cover 11 and the liquid working meson storage tank 2303, and the arrangement is lower than the air pressure balance pipe 2302 in the vertical direction. The air pressure balance pipe 2302 connects the throttle valve return pipe 1701 and the liquid working meson storage tank 2303. The connecting part of the air pressure balance pipe 2302 and the throttle valve return pipe 1701 should be close to the throttle valve body 1702. The connecting part of the air pressure balance pipe 2302 and the liquid working meson storage tank 2303 should be located above the liquid level of the liquid working meson in the liquid working meson storage tank 2303 in the non-working state.

When the brake device of this embodiment is not working, the pressure in the liquid working meson storage tank 2303 is adjusted to atmospheric pressure through the pressure air regulating proportional valve 2304, and the liquid working meson in the internal cavity of the crankshaft body enters through the three-way pipe 2301 The liquid working meson storage tank 2303 partially empties the liquid working meson inside the crankshaft body.

When the brake device is working, after the clutch mechanism is working, the external compressed air enters the liquid working medium storage tank 2303 through the pressure air regulating proportional valve 2304 to increase the pressure in the liquid working meson storage tank 2303, and compress the liquid through the action of air pressure The working meson enters the internal cavity of the crankshaft body through the three-way pipe 2301; at the same time, when the piston 19 without a seal ring moves to the hydraulic cylinder head part 20, the throttle valve part 17 is fully opened, and the internal cavity of the crankshaft body and the working cavity The gas enters the liquid working meson storage tank through the throttle valve part 17 and the throttle valve return pipe 1701 and the air pressure balance pipe 2302. The compression process forms a negative pressure in the cavity inside the crankshaft body, and the liquid working meson is pumped into the working cavity of the body At the same time, when the piston without seal ring moves away from the hydraulic cylinder head part 20, the negative pressure in the working chamber will also pump the liquid working meson into the internal cavity of the crankshaft body and the working cavity, and finally the working meson will fill the inside of the crankshaft body Cavity and working cavity. The braking device began to fully work. This working process, from the compressed air entering the working meson storage tank to the liquid working meson filling the cavity and working cavity inside the crankshaft body, will be completed within 0.3-0.5 seconds.

The invention has the advantages of simple structure, convenient production, flexible installation, less use of liquid working media, high braking efficiency, and good reliability, so that the product cost has obvious advantages compared with the existing products of the same type, and the after-sales maintenance cost is low. The overall cost in the life cycle is more advantageous. Because it will not cause power loss of the external transmission mechanism, thereby reducing energy consumption, it is economical and more environmentally friendly.

Clutch mechanism: The spline of the clutch spline sleeve engages with the spline of the clutch spline half shaft and the crankshaft during operation. It has a simple structure, high reliability, fast response, large transmission torque, and no braking torque loss. In the non-working state, due to the clutch separation, the clutch spline half shaft is in idling state. Compared with the existing similar products, there is no power loss when idling. This improves the efficiency of the external transmission mechanism, improves economy, and reduces energy consumption. More environmentally friendly.

Seal-ring piston connecting rod mechanism (i.e. the above-mentioned transmission mechanism): This structure can realize the circumferential distribution of the hydraulic cylinder assembly within a range of 360 degrees. By changing the number of the hydraulic cylinder assembly, the brake working range of the product is wider. The mechanism has simple structure, convenient manufacture and high versatility. At the same time, because the hydraulic cylinders are symmetrically distributed in 360 degrees, the hydraulic cylinders work at the same time within 360 degrees, and the work is smoother, and there is no axial force generated, so the stability and reliability of the product are better. At the same time, this structure can also realize the horizontal and symmetrical arrangement of two hydraulic cylinders. As shown in Figure 19, by changing the number of horizontal arrangement of hydraulic cylinders, the brake working range is wider and the product layout is more flexible and convenient. Alternatively, it may also be formed in a structure in which a plurality of hydraulic cylinders, for example, four hydraulic cylinders, are arranged in the axial direction.

Hydraulic cylinder assembly mechanism: The mechanism adopts a non-seal ring piston structure, which is easy to process. At the same time, the outer surface of the non-seal ring piston and the hydraulic cylinder body are large in combination with good guidance. The liquid working meson directly acts between the two. Lubrication and sealing function can better adapt to heavy load and high frequency movement. At the same time, the number of parts is reduced and the cost is lower. The hydraulic cylinder head has only the oil outlet design, and the one-way valve design is integrated in the oil outlet direction. The structure is simple and easy to manufacture.

Hydraulic cylinder head components: a one-way valve with a conical seal design, which is designed to be integrated on the cylinder head and has a simple and reliable structure. The spool of the one-way valve adopts a pressure balance hole design with a simple structure to ensure smooth movement of the valve body. This component guarantees the one-way flow of the liquid working meson and avoids backflow. The check valve core adopts a tapered surface seal and an outer diameter stepped design. The part connected with the tapered surface is a small diameter, and the part that matches the inner hole of the cylinder head is a large diameter. The size is formed by the outer circle step. The pressure balance hole is located at the small diameter part of the outer circle. It penetrates the small diameter of the outer circle and the inner hole of the valve core to achieve internal and external pressure balance.

Piston parts: No seal ring design creates a high-pressure oil film between the piston side wall and the cylinder block, reduces the friction between the piston and the cylinder block, balances the lateral torque of the connecting rod to the piston, and improves the reliability of the piston and the cylinder block. Specific examples are shown in Figure 14-18.

Embodiment 1, Figure 14 is one of the design structures of a piston without a seal ring. During the compression process, when the piston moves toward the cylinder head, the liquid working meson flows at high speed between the side wall of the piston and the cylinder to form a high-pressure oil film.

Embodiment 2, Figure 15 is the second design structure of a piston without a seal ring. The structure is that the top surface of the piston and the side wall of the piston are connected in the circumferential direction by a tapered surface of 0-20 degrees formed with the side wall of the piston. During the compression process, when the piston moves toward the cylinder head, the liquid working meson flows through the side wall of the piston and the cylinder at high speed through the guiding action of the tapered surface to form a high-pressure oil film.

Embodiment 3, Figure 16 is the third design structure of a piston without a seal ring. The top of the piston and the side wall of the piston are communicated through the through hole, and the liquid working meson directly acts on the side wall of the piston and the cylinder through the through hole to establish High pressure oil film.

Example 4, Figure 17 is the fourth design structure of a piston without a seal ring. This structure forms a circumferentially distributed annular (belt-shaped) groove on the side wall of the piston. The through hole connects the top of the piston and the side wall of the piston. The annular groove is connected to ensure that the liquid working meson directly enters the annular groove on the side wall of the piston after passing through the through hole, and a stable and uniform high-pressure oil film in the circumferential direction is established through the annular groove.

Example 5, Figure 18 is the fifth design structure of a piston without a seal ring. This structure forms annular (belt-shaped) grooves distributed in the circumferential direction on the side wall of the piston. It communicates with the annular (belt-shaped) groove between the side wall of the piston to ensure that the liquid working meson directly enters the annular groove on the side wall of the piston after passing through the axial groove, and the annular groove establishes stability in the circumferential direction , Uniform high pressure oil film.

Throttle valve mechanism: It is composed of throttle valve inlet pipe, throttle valve body, throttle valve disc and throttle valve outlet pipe. The common rail design of the throttle valve mechanism and the oil inlet pipe connected to the multi-cylinder ensures that the pressure in the oil inlet pipe and the compression cylinders of the liquid working meson is balanced and stable during the compression process, and the force transmitted to the crankshaft connecting rod connecting plate is smooth, thereby making the action The pressure on the bearing and the crankshaft journal is more even, which improves the reliability and service life of the parts, and makes the crankshaft smoother during operation.

Liquid working meson storage tank components: the pressure air adjustment proportional valve 2304 of the storage tank adjusts the gas pressure in the liquid working meson storage tank, thereby increasing the working meson pressure in the internal cavity of the crankshaft body and improving the braking effect of the system. At the same time, the design of the air pressure balance tube can make full use of the reciprocating movement of the piston, which can quickly fill the working chamber with the liquid working meson and improve the braking response speed.

Throttle valve oil inlet pipe common rail structure: the one-way valve of each cylinder head is connected through the common rail oil pipe 25 and then connected with the throttle valve oil inlet pipe 1704 to form a multi-cylinder connected oil inlet pipe common rail structure. The liquid working meson enters the common rail oil pipe after passing through the check valve of the cylinder head, then enters the throttle valve through the throttle valve inlet pipe, and finally returns to the internal cavity of the body through the throttle valve return pipe.

Without departing from the basic characteristics of the present invention, the present invention can be embodied in various forms. Therefore, the embodiments of the present invention are for illustration rather than limitation, because the scope of the present invention is defined by the claims rather than the specification. , And all changes falling within the scope defined by the claims or the equivalent scope of the defined scope shall be understood to be included in the claims.

Claims

A reciprocating piston hydraulic brake device without a seal ring, which is characterized in that it comprises:

A hydraulic cylinder, comprising: a cylinder head, a cylinder block, and a piston without a seal ring capable of reciprocating within the cylinder block;

The clutch mechanism includes: a clutch housing and a crankshaft body connected to each other; a clutch half shaft provided in the clutch housing and a clutch spline sleeve provided outside the clutch half shaft; The crankshaft, and the transmission gear connected with the clutch half shaft; when the clutch mechanism is disconnected, the keys in the clutch spline sleeve cooperate with the teeth of the crankshaft, and when the clutch mechanism works, the clutch spline The keys in the key sleeve simultaneously mesh with the teeth of the clutch half shaft and the teeth of the crankshaft;

The transmission mechanism drives the piston without a seal ring to move.
The reciprocating piston hydraulic brake device without a seal ring according to claim 1, wherein the transmission mechanism includes: a crankshaft connecting rod connecting plate connected to the crankshaft, connected to the crankshaft connecting rod connecting plate The connecting rod pin, the connecting rod connected with the connecting rod pin, and the piston pin connected with the connecting rod, the piston pin is connected with the seal-less piston to drive its movement.
The reciprocating piston hydraulic brake device without a seal ring according to claim 1, wherein the transmission mechanism includes a main connecting rod and an auxiliary connecting rod, and the main connecting rod is divided into a connecting rod small end and a connecting rod. Rod, connecting rod big end; the small end of the connecting rod is provided with a piston pin hole, the big end of the connecting rod is provided with an auxiliary connecting rod connecting hole for inserting the auxiliary connecting rod; the connecting rod pin penetrates the auxiliary connection of the big end of the connecting rod The rod connecting hole and the auxiliary connecting rod are connected with the main connecting rod; the small end of the connecting rod and the other end of the auxiliary connecting rod are connected with the non-seal ring piston through a piston pin.
The reciprocating seal-less piston hydraulic brake device according to claim 1, wherein the clutch mechanism further includes a clutch half shaft thrust plate that restricts movement of the clutch half shaft and restricts the crankshaft axial direction Moving crankshaft axial thrust plate.
The reciprocating type seal-less piston hydraulic brake device according to claim 1 or 2, wherein the clutch mechanism further includes a clutch dial that pushes the clutch spline sleeve to move toward the clutch half shaft. Fork assembly.
A reciprocating piston hydraulic brake device without a seal ring, which is characterized in that it comprises:

A hydraulic cylinder, comprising: a cylinder head, a cylinder block, and a piston without a seal ring capable of reciprocating within the cylinder block;

A clutch mechanism includes: a clutch housing and a crankshaft body connected to each other, the crankshaft body is provided with a crankshaft; the force generated by the compression and pumping of the seal-less piston is transmitted to the crankshaft through the reaction torque The clutch mechanism is transmitted to the main shaft of the power plant;

A transmission mechanism that drives the piston without a seal ring to move and includes a crankshaft connecting rod connecting plate connected to the crankshaft, a connecting rod pin connected to the crankshaft connecting rod connecting plate, and a connecting rod connected to the connecting rod pin , A piston pin connected with the connecting rod, the piston pin is connected with the piston without a seal ring to drive its movement.
A reciprocating piston hydraulic brake device without a seal ring, which is characterized in that it comprises:

A hydraulic cylinder, comprising: a cylinder head, a cylinder block, and a piston without a seal ring capable of reciprocating within the cylinder block;

A clutch mechanism includes: a clutch housing and a crankshaft body connected to each other, the crankshaft body is provided with a crankshaft; the force generated by the compression and pumping of the seal-less piston is transmitted to the crankshaft through the reaction torque The clutch mechanism is transmitted to the main shaft of the power plant;

The transmission mechanism drives the piston without seal ring to move, and is provided with: a main connecting rod and an auxiliary connecting rod. The main connecting rod is divided into a connecting rod small end, a connecting rod, and a connecting rod large end; the connecting rod small end is provided with a piston A pin hole, the connecting rod head is provided with a secondary connecting rod connecting hole for inserting the secondary connecting rod; the connecting rod pin penetrates the secondary connecting rod connecting hole of the connecting rod head and the secondary connecting rod is connected with the main connecting rod; The small end of the connecting rod and the other end of the auxiliary connecting rod are connected with the piston without a seal ring through a piston pin.
The reciprocating piston hydraulic brake device without a seal ring according to any one of claims 1 to 7, further comprising a crankshaft body cover plate connected with the crankshaft body to form a closed internal cavity of the crankshaft body .
The reciprocating piston hydraulic brake device without a seal ring according to claim 8, further comprising a cooling water channel independent of the internal cavity of the crankshaft body.
The reciprocating piston hydraulic brake device without a seal ring according to claim 8, wherein a throttle valve inlet pipe, a throttle valve component, and a throttle valve are connected between the cylinder head and the internal cavity of the crankshaft body. Throttle valve return pipe.
The reciprocating piston hydraulic brake device without a seal ring according to any one of claims 1 to 10, wherein the side wall of the piston without seal ring is provided with a high pressure groove for a liquid working meson.
The reciprocating piston hydraulic brake device without a seal ring according to any one of claims 1 to 11, wherein the clutch spline sleeve has splines inside, and the clutch spline sleeve The tooth profile angle at the end is 0-30 degrees.
The reciprocating piston hydraulic brake device without a seal ring according to any one of claims 1 to 12, wherein there is a gap between the side wall of the seal ringless piston and the cylinder block.
The reciprocating piston hydraulic brake device without a seal ring according to claim 8, characterized in that it further comprises a liquid working meson storage box component, and the liquid working meson storage box component includes a three-way pipe, an air pressure balance pipe, The liquid working meson storage tank box and the pressure air regulating proportional valve, the three-way pipe is located at the bottom of the crankshaft body cover and the liquid working meson storage tank box, and is lower than the air pressure balance pipe in the vertical direction; The air pressure balance pipe connects the throttle valve oil return pipe and the liquid working meson storage tank body, and the part connected with the throttle valve oil return pipe is close to the throttle valve body; the air pressure balance pipe and the liquid working meson storage tank body The connecting part is located above the liquid level of the liquid working meson in the liquid working meson storage tank in the non-working state.
The reciprocating piston hydraulic brake device without a seal ring according to claim 10, wherein the cylinder head is provided with a one-way valve, and the one-way valve of each of the plurality of hydraulic cylinders passes through a common rail oil pipe After connection, it is connected with the throttle valve oil inlet pipe to form a common rail structure of the oil inlet pipe with multi-cylinder communication.
The reciprocating piston hydraulic brake device without a seal ring according to any one of claims 1 to 15, wherein the cylinder head is provided with a one-way valve, and the one-way valve includes a stepped outer diameter The check valve spool is provided with a check valve pressure balance hole at the outer diameter portion of the check valve spool to penetrate the outer diameter portion and the inner hole of the valve core.
The reciprocating hydraulic brake device for a piston without a seal ring according to any one of claims 1 to 16, wherein the side wall of the piston without a seal ring is formed with annular grooves distributed in a circumferential direction.